Combustion control device for gas turbine

ABSTRACT

A combustion control device for a gas turbine is capable of controlling fuel ratios such as a pilot ratio and controlling an aperture of a combustor bypass valve in response to a combustion gas temperature at an inlet of the gas turbine in accordance with the original concept by computing a combustion load command value which is proportional to the combustion gas temperature. The combustion control device is configured to calculate a 700° C. MW value and a 1500° C. MW value based on an inlet guide vane aperture, an intake-air temperature, and an atmospheric pressure ratio, then to calculate the combustion load command value to render the combustion gas temperature at the inlet of the gas turbine dimensionless by direct interpolation based on these values and an actual measurement value of a power generator output, and to control apertures of a pilot fuel flow rate control valve, a top hat fuel flow rate control valve, and a main fuel flow rate control valve based on ratios of fuel gas to be determined based on this combustion load command value, and thereby to control fuel supplies to a pilot nozzle, a top hat nozzle, and a main nozzle.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a combustion control device for a gasturbine.

2. Background Art

A gas turbine typically includes a gas turbine body, a combustor, acompressor provided with inlet guide vanes (IGVs), and fuel flow ratecontrol valves for controlling fuel supplies to fuel nozzles of thecombustor. Such a gas turbine further includes a combustion controldevice for the gas turbine which is configured to control the fuelsupplies to the fuel nozzles by controlling apertures of the fuel flowrate control valves, and an IGV control device configured to controlapertures of the IGVs.

Moreover, the combustor may include one provided with multiple types offuel nozzles, one provided with a main nozzle for premixed combustionand a pilot nozzle for diffuse combustion in order to reduce NOx at thetime of high-load combustion and to achieve combustion stability at thetime of low-load combustion, and one further provided with a top hatnozzle for premixed combustion in order to enhance NOx reduction and thelike.

FIG. 39 is a block diagram showing an outline of a process flow in termsof a conventional gas turbine combustion control device. As shown inFIG. 39, the conventional gas turbine combustion control device isconfigured to set up a valve position command value (CSO) in the firstplace based on a power generator output command value transmitted from acentral load dispatching center for managing power generator outputs interms of multiple power generation facilities. Then, a pilot fuel flowrate control valve position command value (PLCSO), a top hat fuel flowrate (THCSO), and a main fuel flow rate control valve position commandvalue (MACSO) are calculated based on this CSO, a function FX1 of theCSO and the PLCSO set up to obtain a given pilot ratio, a function FX2of the CSO and the THCSO set up to obtain a given top hat ratio, and acalculation formula (MACSO=CSO−PLCSO−THCSO) for finding the MACSO. Afuel supply to the main nozzle, a fuel supply to the pilot nozzle, and afuel supply to the top hat nozzle are controlled by regulating anaperture of a main fuel flow rate control valve, an aperture of a pilotflow rate control valve, and an aperture of a top hat control valverespectively based on these valve position command values, and therebycontrolling the power generator output to match the power generatoroutput command value. If an actual measurement value of the powergenerator output does not match the power generator output command valuein this case, the gas turbine combustion control device adjusts the CSObased on deviations of these factors so as to achieve matching.

Meanwhile, when the gas turbine includes a combustor bypass valve foradjusting a bypass amount of compressed air to the combustor, theconventional combustion control device for the gas turbine calculates acombustor bypass valve position command value (BYCSO) based on afunction (BYCSO=FX(MW/Pcs)) of a ratio (MW/FX(Pcs)) between a powergenerator output (a gas turbine output) MW and a function FX(Pcs) of acylinder pressure Pcs and the BYCSO, as well as on a ratio (MW/FX(Pcs))between an actual measurement value of the power generator output (thegas turbine output) MW and the function FX(Pcs) of an actual measurementvalue of the cylinder pressure Pcs as shown in FIG. 40. The bypassamount of the compressed air has been regulated by controlling anaperture of the combustor bypass valve based on this BYCSO. That is, inthis case, a state of combustion of the gas turbine is regulated byperforming the above-mentioned two control operations (i.e., the fuelflow rate control valve position control and the combustor bypass valveposition control).

Of the following prior art documents, Patent Publication 1 discloses apilot ratio automatic control device, Patent Publication 2 discloses agas turbine fuel supply device, and Patent Publication 3 discloses acombustion control device, respectively.

(Patent Document 1) Japanese Unexamined Patent Publication No.11(1999)-22490

(Patent Document 2) Japanese Unexamined Patent Publication No.8(1996)-178290

(Patent Document 3) Japanese Unexamined Patent Publication No.6(1994)-147484

The above-described conventional gas turbine combustion control devicecalculates the valve position command values (PLCSO, THCSO, and MACSO)of the respective fuel flow rate control valves directly by use of theCSO (the valve position command value). Specifically, the pilot ratio,the top hat ratio, and so forth are controlled as the functions of theCSO (the valve position command value). Moreover, the aperture of thecombustor bypass valve is controlled as a function of the ratio(MW/FX(Pcs)) between the power generator output (the gas turbine output)MW and the function FX(Pcs) of the cylinder pressure Pcs. For thisreason, the conventional gas turbine combustion control device has thefollowing problems.

-   1. Even in an operating state where a combustion gas temperature at    an inlet of a gas turbine is constant, a change in an intake-air    temperature (an atmospheric temperature) leads to a change in the    density of the intake-air. Such a change causes variations in the    CSO and MW/FX(Pcs), whereby the pilot ratio, the top hat ratio, the    aperture of the combustor bypass valve, and the like also change. If    the intake-air temperature changes as shown in an example of a    relation between a combustion gas temperature TIT at an inlet of a    gas turbine and the CSO relative to the variation in the intake-air    temperature in FIG. 41, the relation between the combustion gas    temperature TIT at the inlet of the gas turbine and the CSO is    deviated. Moreover, when the CSO is deviated, the PLCSO, the THCSO    and the like are also deviated. As a consequence, the pilot ratio,    the top hat ratio, and the like are also deviated.-   2. Even in the operating state where the combustion gas temperature    at the inlet of the gas turbine is constant, a change in a fuel gas    temperature leads to a change in the density of the fuel gas. Such a    change causes a variation in the CSO, whereby the pilot ratio, the    top hat ratio, and the like also change. If the fuel gas temperature    changes as shown in an example of a relation between the combustion    gas temperature TIT at the inlet of the gas turbine and the CSO    relative to the variation in the fuel gas temperature in FIG. 42,    the relation between the combustion gas temperature TIT at the inlet    of the gas turbine and the CSO is deviated. Moreover, when the CSO    is deviated, the PLCSO, the THCSO and the like are also deviated. As    a consequence, the pilot ratio, the top hat ratio, and the like are    also deviated.-   3. Even in the operating state where the combustion gas temperature    at the inlet of the gas turbine is constant, a change in the    performance of the gas turbine attributable to deterioration in    capabilities of a compressor or the like causes the variations in    the CSO and MW/FX(Pcs), whereby the pilot ratio, the top hat ratio,    the aperture of the combustor bypass valve, and the like also    change.-   4. Even in the operating state where the combustion gas temperature    at the inlet of the gas turbine is constant, a change in the    property of the fuel gas (a calorific value of the fuel gas) causes    the variation in the CSO, whereby the pilot ratio, the top hat    ratio, the aperture of the combustor bypass valve, and the like also    change. If the calorific value of the fuel gas changes as shown in    an example of a relation between the gas turbine output (the power    generator output) and the CSO relative to the variation in the    calorific value of the fuel gas in FIG. 43, the relation between gas    turbine output (the power generator output) and the CSO is deviated.    Moreover, when the CSO is deviated, the PLCSO, the THCSO and the    like are also deviated. As a consequence, the pilot ratio, the top    hat ratio, and the like are also deviated.-   5. Moreover, the ratios such as the pilot ratio and the BYCSO    involve mutually different control parameters.

In short, the pilot ratio, the top hat ratio, the main ratio, and theaperture of the combustor bypass valve are supposed to be controlledbased on the combustion gas temperature at the inlet of the gas turbine.However, the above-mentioned problems may occur because the conventionalcombustion control device for a gas turbine does not perform the controlbased on the combustion gas temperature at the inlet of the gas turbine.Nevertheless, the combustion gas temperature at the inlet of the gasturbine becomes extremely high (a maximum combustion gas temperaturereaches 1500° C., for example). Under the circumstances, it is notpossible to obtain a thermometer which can measure such a highcombustion gas temperature at the inlet of the gas turbine for a longtime period. As a consequence, it is not possible to control the pilotratio, the top hat ratio, the main ratio, and the aperture of thecombustor bypass valve based on the actual measurement value of thecombustion gas temperature at the inlet of the gas turbine.

SUMMARY OF THE INVENTION

The present invention has been made in consideration of the foregoingproblems. An object of the present invention is to provide a combustioncontrol device for a gas turbine capable of controlling fuel ratios suchas a pilot ratio and controlling an aperture of a combustor bypass valvein response to a combustion gas temperature at an inlet of a gas turbinein accordance with the original concept by computing a combustion loadcommand value (CLCSO) which is proportional to the combustion gastemperature at the inlet of the gas turbine.

To attain the object, a first aspect of the present invention provides acombustion control device for a gas turbine which is fitted to a gasturbine provided with a gas turbine body, a combustor having multipletypes of fuel nozzles, a compressor having an inlet guide vane, andmultiple fuel flow rate control valves for respectively controlling fuelsupplies to the multiple types of the fuel nozzles, and is configured tocontrol the fuel supplies to the multiple types of the fuel nozzles bycontrolling apertures of the fuel flow rate control valves. Here, thecombustion control device includes first gas turbine output computingmeans for computing a first gas turbine output corresponding to a firstcombustion gas temperature at an inlet of the gas turbine based on anintake-air temperature of the compressor and an aperture of the inletguide vane, second gas turbine output computing means for computing asecond gas turbine output corresponding to a second combustion gastemperature at the inlet of the gas turbine higher than the firstcombustion gas temperature at the inlet of the gas turbine based on theintake-air temperature of the compressor and the aperture of the inletguide vane, and combustion load command computing means for computing acombustion load command value to render the combustion gas temperaturedimensionless by direct interpolation based on the first gas turbineoutput computed by the first gas turbine output computing means, thesecond gas turbine output computed by the second gas turbine outputcomputing means, and an output of the gas turbine. Here, ratios of fuelsto be supplied respectively to the multiple types of the fuel nozzlesare determined based on the combustion load command value computed bythe combustion load command computing means, and the fuel supplies tothe multiple types of the fuel nozzles are controlled by controllingapertures of the fuel flow rate control valves based on the ratio of thefuels.

Meanwhile, a second aspect of the present invention provides thecombustion control device for a gas turbine according to the firstaspect, in which the gas turbine includes a combustor bypass valve foradjusting a bypass amount of compressed air to the combustor, and thebypass amount of the compressed air is regulated by controlling anaperture of the combustor bypass valve based on the combustion loadcommand value computed by the combustion load command computing means.

Meanwhile, a third aspect of the present invention provides thecombustion control device for a gas turbine according to any one of thefirst and second aspects, in which the gas turbine includes gas turbinebypassing means for bypassing compressed air to any of the combustor andthe gas turbine body. Here, the first gas turbine output computing meanscomputes the first gas turbine output based on the intake-airtemperature of the compressor, the aperture of the inlet guide vane, anda turbine bypass ratio equivalent to a ratio between a total amount ofcompressed air by the compressor and a turbine bypass flow rate by thegas turbine bypassing means, and the second gas turbine output computingmeans computes the second gas turbine output based on the intake-airtemperature of the compressor, the aperture of the inlet guide vane, andthe turbine bypass ratio.

Meanwhile, a fourth aspect of the present invention provides thecombustion control device for a gas turbine according to any one of thefirst, second, and third aspects, in which the first gas turbine outputcomputing means computes the first gas turbine output based on theintake-air temperature of the compressor, the aperture of the inletguide vane, and an atmospheric pressure ratio equivalent to a ratiobetween an intake pressure of the compressor and a standard atmosphericpressure or computes the first gas turbine output based on theintake-air temperature of the compressor, the aperture of the inletguide vane, the turbine bypass ratio, and the atmospheric pressureratio. Moreover, the second gas turbine output computing means computesthe second gas turbine output based on the intake-air temperature of thecompressor, the aperture of the inlet guide vane, and the atmosphericpressure ratio or computes the second gas turbine output based on theintake-air temperature of the compressor, the aperture of the inletguide vane, the turbine bypass ratio, and the atmospheric pressureratio.

Meanwhile, a fifth aspect of the present invention provides thecombustion control device for a gas turbine according to any one of thefirst, second, third, and fourth aspects, which further includesintake-air temperature correcting means for correcting the ratios offuels based on the intake-air temperature of the compressor.

Meanwhile, a sixth aspect of the present invention provides thecombustion control device for a gas turbine according to the fifthaspect, in which the intake-air temperature correcting means adjusts anintake-air temperature correction amount in response to the combustionload command value.

Meanwhile, a seventh aspect of the present invention provides thecombustion control device for a gas turbine according to any one of thefirst, second, third, fourth, fifth, and six aspects, in which thesecond gas turbine output computing means computes the second gasturbine output corresponding to a maximum combustion gas temperatureequivalent to the second combustion gas temperature at the inlet of thegas turbine, and the combustion control device includes learning meansfor comparing the first gas turbine output computed by the second gasturbine output computing means and an output of the gas turbine after ajudgment that the combustion gas temperature at the inlet of the gasturbine reaches the maximum combustion gas temperature based on atemperature of exhaust gas discharged from the gas turbine body and on apressure ratio of the compressor, and correcting the first gas turbineoutput so as to coincide with the output of the gas turbine.

Here, when controlling the apertures of the fuel flow rate controlvalves based on the ratios of the fuels (including a pilot ratio, a tophat ratio, and a main ratio, for example) as defined in the first aspectof the invention, it is possible to control the apertures by arbitrarycontrolling means. For example, the following configurations areapplicable in this case.

Specifically, a combustion control device for a gas turbine of a firstconfiguration provides the combustion control device for a gas turbineaccording to any one of the first to seventh aspects, which includesfuel ratio setting means for calculating the ratios of fuels to besupplied respectively to the multiple types of fuel nozzles based on thecombustion load command value computed by the combustion load computingmeans and a function of the combustion load command value and the ratioof fuel, fuel flow rate command setting means for calculating fuel flowrate command values proportional to fuel flow rates to be suppliedrespectively to the multiple types of the fuel nozzles based on a totalfuel flow rate command value proportional to a total fuel flow rate tobe supplied to the multiple types of the fuel nozzles and on the ratiosof fuels, fuel flow rate setting means for calculating the fuel flowrates to be supplied respectively to the multiple types of the fuelnozzles based on the fuel flow rate command values set up by the fuelflow rate command setting means and on a function of the fuel flow ratecommand values and the fuel flow rates, Cv value setting means forcalculating Cv values of the fuel flow rate control valves in accordancewith a Cv value formula based on the fuel flow rates set up by the fuelflow rate setting means, a fuel temperature, and front pressures andback pressures of the fuel flow rate control valves, and fuel flow ratecontrol valve position command setting means for calculating fuel flowrate control valve position command values based on the Cv values set upby the Cv value setting means and on a function of the Cv values andfuel flow rate control valve positions. Here, the fuel supplies to themultiple types of the fuel nozzles are controlled by regulatingapertures of the fuel flow rate control valves based on the fuel flowrate control valve position command values set up by the fuel flow ratecontrol valve position command setting means.

Meanwhile, a combustion control device for a gas turbine of a secondconfiguration provides the combustion control device for a gas turbineof the first configuration, which further includes fuel temperaturecorrecting means for using a measurement value of the fuel temperatureat a certain time period prior to occurrence of an anomaly of a fuelthermometer for measuring the fuel temperature as the fuel temperaturein the event of the anomaly.

Meanwhile, a combustion control device for a gas turbine of a thirdconfiguration provides the combustion control device for a gas turbineof the second configuration, in which the fuel temperature correctingmeans includes a first primary delay operator and a second primary delayoperator including a smaller primary delay time constant than a primarydelay time constant of the first primary delay operator. Here, primarydelay calculations are performed by use of the first primary delayoperator and the second primary delay operator in terms of the fueltemperature, and a smaller value of calculation results is used as thefuel temperature.

Meanwhile, a combustion control device for a gas turbine of a fourthconfiguration provides the combustion control device for a gas turbineof any one of the first, second, and third configurations, which furtherincludes pressure computing means for computing a back pressure of thefuel flow rate control valve corresponding to a front pressure of thefuel nozzle by use of a formula for computation of the front pressurebased on the fuel flow rate of the fuel nozzle derived from the fuelflow rate set up by the fuel flow rate setting means, the Cv value ofthe fuel nozzle, the fuel temperature, and a back pressure of the fuelnozzle, and pressure correcting means for using the pressure computed bythe pressure computing means as the back pressure of the fuel flow ratecontrol valve upon occurrence of an anomaly of a pressure gauge formeasuring the back pressure of the fuel flow rate control valve.

Meanwhile, a combustion control device for a gas turbine of a fifthconfiguration provides the combustion control device for a gas turbineof the fourth configuration, which includes learning means for comparingthe back pressure of the fuel flow rate control valve computed by thepressure computing means with an actual measurement value of the backpressure of the fuel flow rate control valve and correcting the Cv valueof the fuel nozzle such that the computed value of the back pressurecoincides with the actual measurement value of the back pressure.

According to the combustion control device for a gas turbine of thefirst aspect of the present invention, the first gas turbine output andthe second gas turbine output are computed based on the aperture of theinlet guide vane and the intake-air temperature. Then, the CLCSOrendering the combustion gas temperature at the inlet of the gas turbinedimensionless is computed by use of direct interpolation based on thefirst gas turbine output, the second gas turbine output, and the gasturbine output. Thereafter, the fuel supplies to the respective fuelnozzles are controlled by controlling apertures of the respective fuelflow rate control valves based on the ratio of the fuels determinedbased on this CLCSO. Accordingly, it is possible to perform the controlbased on the combustion gas temperature at the inlet of the gas turbinein conformity to the original concept, and to maintain relations betweenthe combustion load command value and the respective fuel gas ratios,i.e. relations between the combustion gas temperature at the inlet ofthe gas turbine and the respective fuel gas ratios even if theintake-air temperature, the combustion gas temperature, and theproperties of the combustion gas are changed or if the performance ofthe gas turbine is deteriorated. As a result, it is possible to performmore appropriate combustion control than that of a conventionalcombustion control device.

Moreover, according to the combustion control device for a gas turbineof the second aspect of the present invention, the bypass amount of thecompressed air is controlled by regulating the aperture of the combustorbypass valve based on the combustion load command value computed by thecombustion load command computing means. Accordingly, it is possible tocontrol the combustor bypass valve based on the combustion gastemperature at the inlet of the gas turbine in conformity to theoriginal concept as well. Moreover, it is possible to maintain arelation between the combustion load command value and the aperture ofthe combustor bypass valve, i.e. a relation between the combustion gastemperature at the inlet of the gas turbine and the aperture of thecombustor bypass valve. As a result, it is possible to perform moreappropriate combustion control than a conventional combustion controldevice in light of the bypass flow rate control of the compressed air aswell.

Further, according to the combustion control device for a gas turbine ofthe third aspect of the present invention, the combustion load commandvalue is computed in consideration of the turbine bypass ratio as well.Accordingly, it is also possible to control the gas turbine providedwith the gas turbine bypassing means based on the combustion gastemperature at the inlet of the gas turbine. Moreover, it is possible tomaintain relations between the combustion load command value (thecombustion gas temperature at the inlet of the gas turbine) and therespective ratios of fuel gas even if the intake-air temperature, thecombustion gas temperature, and the properties of the combustion gas arechanged or if the performance of the gas turbine is deteriorated. As aresult, it is possible to perform more appropriate combustion controlthan that of a conventional combustion control device.

Moreover, according to the combustion control device for a gas turbineof the fourth aspect of the present invention, it is possible to computethe combustion load command value in consideration of the atmosphericpressure ratio as well, and thereby to maintain the relations betweenthe combustion load command value (the combustion gas temperature at theinlet of the gas turbine) and the respective ratios of fuel gas moreappropriately. As a result, it is possible to perform more appropriatecombustion control.

Moreover, according to the combustion control device for a gas turbineof the fifth aspect of the present invention, the ratios of fuel arecorrected based on the intake-air temperature of the compressor. As aresult, it is possible to perform more appropriate combustion control inresponse to the variation in the intake-air temperature.

Meanwhile, according to the combustion control device for a gas turbineof the sixth aspect of the present invention, the intake-air temperaturecorrection amount is adjusted in response to the combustion load commandvalue. As a result it is possible to perform appropriate intake-airtemperature correction in response to the load (the gas turbine output).

In addition, the combustion control device for a gas turbine of theseventh aspect of the present invention includes the learning means,which is configured to compare the first gas turbine output computed bythe second gas turbine output computing means and the output of the gasturbine after the judgment that the combustion gas temperature reachesthe maximum combustion gas temperature based on the temperature ofexhaust gas discharged from the gas turbine body and on the pressureratio of the compressor, and to correct the first gas turbine output soas to coincide with the output of the gas turbine. As a result, even ifthe performance of the gas turbine is deteriorated, it is possible tomaintain the relations between the combustion load command value (thecombustion gas temperature at the inlet of the gas turbine) and therespective ratios of fuel gas and the relation between the combustionload command value (the combustion gas temperature at the inlet of thegas turbine) and the aperture of the combustor bypass valve.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a view showing a schematic configuration of a gas turbineincluding a combustion control device for a gas turbine according to anembodiment of the present invention.

FIG. 2 is a view showing a structure of a combustor in the gas turbine.

FIG. 3 is a block diagram showing a pilot manifold portion of a pilotfuel supply line in the gas turbine.

FIG. 4 is an overall block diagram showing the combustion control devicefor a gas turbine according to the embodiment of the present invention.

FIG. 5 is a block diagram showing an outline of a process flow in thecombustion control device for a gas turbine.

FIG. 6 is a graph showing a relation between a combustion gastemperature TIT at an inlet of the gas turbine and a CLCSO.

FIG. 7 is a graph showing a relation between the CLCSO and a pilotratio.

FIG. 8 is a graph showing a relation between the CLCSO and a top hatratio.

FIG. 9 is a graph showing a relation between the CLCSO and a combustorbypass valve position command value.

FIG. 10 is a graph showing a relation between the combustion gastemperature TIT at the inlet of the gas turbine and a gas turbine output(a power generator output) in terms of various IGV apertures.

FIG. 11 is a graph showing a relation between an intake-air temperatureand the gas turbine output (the power generator output) in terms of thevarious IGV apertures.

FIG. 12 is a graph showing a relation between the power generator output(the gas turbine output9 at a certain IGV aperture, a certain intake-airtemperature, a certain turbine bypass ratio and a certain atmosphericpressure ratio, and the CLCSO.

FIG. 13 is a graph showing the relation between the power generatoroutput (the gas turbine output) and the CLCSO relative to a variation inthe IGV aperture.

FIG. 14 is a graph showing the relation between the power generatoroutput (the gas turbine output) and the CLCSO relative to a variation inthe intake-air temperature.

FIG. 15 is a graph showing the relation between the power generatoroutput (the gas turbine output) and the CLCSO relative to a variation inthe turbine bypass ratio.

FIG. 16 is a block diagram showing a configuration of computation logicof the CLCSO in the combustion control device for a gas turbine.

FIG. 17 is a block diagram showing a configuration of a learning circuitfor a temperature regulated MW in the combustion control device for agas turbine.

FIG. 18 is a graph showing a relation between a pressure ratio of acompressor and an exhaust-gas temperature.

FIG. 19 is a block diagram showing a configuration of computation logicof the combustor bypass valve position command value in the combustioncontrol device for a gas turbine.

FIG. 20 is a graph showing a relation between the CLCSO and weight ofintake-air temperature correction.

FIG. 21 is a graph showing a relation between the intake-air temperatureand a correction coefficient.

FIG. 22 is a block diagram showing a configuration of computation logicof a PLCSO in the combustion control device for a gas turbine.

FIG. 23 is a block diagram showing a configuration of computation logicof a THCSO in the combustion control device for a gas turbine.

FIG. 24 is a block diagram showing a configuration of computation logicof respective fuel flow rate control valve position command values inthe combustion control device for a gas turbine.

FIG. 25 is a graph showing a relation (a proportional relation) betweenthe PLCSO and a pilot fuel gas flow rate G_(fPL).

FIG. 26 is a graph showing a relation between a valve aperture and a Cvvalue.

FIG. 27 is a graph showing a relation (a proportional relation) betweenthe THCSO and a top hat fuel gas flow rate G_(fTH).

FIG. 28 is a graph showing a relation (a proportional relation) betweena MACSO and a main fuel gas flow rate G_(fMA).

FIG. 29 is a block diagram showing a configuration of fuel gastemperature correction logic in the combustion control device for a gasturbine.

FIG. 30 is a block diagram showing a configuration of manifold pressurecorrection logic in the combustion control device for a gas turbine.

FIG. 31 is a graph showing a relation between the power generator output(the gas turbine output) and a change rate.

FIG. 32 is a block diagram showing a configuration of computation logicof a manifold pressure in the combustion control device for a gasturbine.

FIG. 33 is a logic diagram showing a configuration of a learning circuitfor a nozzle Cv value in the combustion control device for a gasturbine.

FIG. 34 is a graph showing operating results of the gas turbineincluding the combustion control device for a gas turbine.

FIG. 35 is another graph showing operating results of the gas turbineincluding the combustion control device for a gas turbine.

FIG. 36 is still another graph showing operating results of the gasturbine including the combustion control device for a gas turbine.

FIG. 37 is still another graph showing operating results of the gasturbine including the combustion control device for a gas turbine.

FIG. 38 is still another graph showing operating results of the gasturbine including the combustion control device for a gas turbine.

FIG. 39 is a block diagram showing an outline of a process flow in aconventional combustion control device for a gas turbine.

FIG. 40 is a graph showing a function of a ratio (MW/FX(Pcs)) between apower generator output (a gas turbine output) MW and a function FX(Pcs)of a cylinder pressure Pcs, and a BYCSO (a combustor bypass valveposition command value).

FIG. 41 is a graph showing a relation between a combustion gastemperature TIT at an inlet of a gas turbine and a CSO relative to avariation in an in-take air temperature.

FIG. 42 is a graph showing a relation between the combustion gastemperature TIT at the inlet of the gas turbine and the CSO relative toa variation in a fuel gas temperature.

FIG. 43 is a graph showing a relation between the gas turbine output(the power generator output) and the CSO relative to a variation in acalorific value of the fuel gas.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

Now, an embodiment of the present invention will be described in detailwith reference to the accompanying drawings.

(Configuration)

Firstly, a configuration of a gas turbine will be described withreference to FIG. 1 to FIG. 3. As shown in FIG. 1, a gas turbine 1includes a gas turbine body 2, multiple combustors 3, and a compressor 4having a rotating shaft joined to a rotating shaft of the gas turbinebody 2. A power generator 5 is installed in this gas turbine 1 tocollectively constitute a gas turbine power generation facility. Arotating shaft of this power generator 5 is also joined to the rotatingshaft of the gas turbine body 2.

Therefore, a fuel is combusted in each of the combustors 3 together witha high-pressure compressed air taken in and compressed by the compressor4. When the gas turbine body 2 is rotated by this combustion gas, thepower generator 5 is driven rotatively by this gas turbine body 2 togenerate power. The power generated by the power generator 5 istransmitted through an unillustrated power transmission system. Thecombustion gas (exhaust gas) discharged from the gas turbine body 2after working the gas turbine body 2 is carried through an exhaust line32 and released from an unillustrated stack to the air. An air-intakeamount of the compressor in the course of this gas turbine drive iscontrolled by opening and closing inlet guide vanes (IGVs) 6 installedat an inlet of the compressor 4. The opening and closing drives of theIGVs 6 are carried out by an actuator 7 such as a servo motor, which isfitted to the IGVs 6. Aperture control of the IGVs 6 (drive control ofthe actuator 7) is performed by an unillustrated IGV control device.

Meanwhile, each of the combustors 3 is provided with a combustor bypassline 31 for causing the air compressed by the compressor 4 to bypass thecombustor 3. The combustor bypass line 31 is provided with a combustorbypass valve 8 for adjusting a bypassing flow rate of the compressedair. At the time of a low load, an aperture of the combustor bypassvalve 8 is increased and the bypassing flow rate of the compressed airis thereby increased in order to raise the fuel gas density and tostabilize combustion. On the contrary, at the time of a high load, theaperture of the combustor bypass valve 8 is reduced and the bypassingflow rate of the compressed air is thereby reduced in order to decreaseNOx and the like. In this way, the amount of the compressed air to bemixed with the combustion gas is increased. Meanwhile, a turbine bypassline 9 for causing the air compressed by the compressor 4 to by pass thecombustor 3 and the gas turbine body 2 is provided in a space from anoutlet side of the compressor to an outlet side (the exhaust line 32) ofthe gas turbine body 2. This turbine bypass line 9 is provided with aturbine bypass valve 10 for adjusting a turbine bypass flow rate of thecompressed air (gas turbine bypassing means). This valve is provided forthe purpose of adjusting an output pressure of the compressor 4 (acylinder pressure) and the like.

Each of the combustors 3 has a configuration as shown in FIG. 2. Asshown in FIG. 2, the combustor 3 includes multiple types of fuelnozzles, namely, main nozzles 26 as first fuel nozzles, a pilot nozzle25 as a second fuel nozzle, and top hat nozzles 27 as third fuelnozzles. The pilot nozzle 25 and the main nozzles 26 are disposed insidean inner cylinder 28, while the top hat nozzles 27 are disposed in aspace between the inner cylinder 28 and an outer cylinder 29.

The pilot nozzle 25 is a fuel nozzle for diffuse combustion targeted forachieving combustion stability and the like. The single pilot nozzle 25is provided at a central part of the inner cylinder 28. The main nozzle26 is a fuel nozzle for premixed combustion targeted for NOx reduction,which is designed to mix main fuel gas with the compressed air on anupstream side of a combustion portion and then to subject the mixed gasto combustion. The multiple main nozzles 26 are provided around thepilot nozzle 25. The top hat nozzle 27 is a fuel nozzle for premixedcombustion targeted for further NOx reduction, which is designed to mixtop hat fuel gas with the compressed air on an upstream side of the mainnozzles 26 and then to subject the mixed gas to combustion. The multipletop hat nozzles 27 are provided on the outer peripheral side of the mainnozzles 26.

Moreover, as shown in FIG. 1 and FIG. 2, a main fuel supply line 12, apilot fuel supply line 13, and a top hat fuel supply line 14 which arebranched off from a fuel gas supply line 11 connected to anunillustrated fuel tank or gas field are connected respectively to themain nozzles 26, the pilot nozzle 25, and the top hat nozzles 27 of eachof the combustors 3. The main fuel supply line 12 is provided with amain fuel pressure control valve 16 and a main fuel flow rate controlvalve 17 in the order from the upstream side. The pilot fuel supply line13 is provided with a pilot fuel pressure control valve 18 and a pilotfuel flow rate control valve 19 in the order from the upstream side.Moreover, the top hat fuel supply line 14 is provided with a top hatfuel pressure control valve 20 and a top hag fuel flow rate controlvalve 21 in the order from the upstream side.

A main manifold 22 of the main fuel supply line 12 is provided with amain manifold pressure gauge PX1 for measuring a pressure of the mainfuel gas inside the main manifold 22. A pilot manifold 23 of the pilotfuel supply line 13 is provided with a pilot manifold pressure gauge PX2for measuring a pressure of pilot fuel gas inside the pilot manifold 23.Moreover, a top hat manifold 24 of the top hat fuel supply line 14 isprovided with a top hat manifold pressure gauge PX3 for measuring apressure of the top hat fuel gas inside the top hat manifold 24.

Meanwhile, the main fuel supply line 12 is provided with a main fueldifferential pressure gauge PDX1 for measuring a main fuel gasdifferential pressure in front and on the back of the main fuel flowrate control valve 17. The pilot fuel supply line 13 is provided with apilot fuel differential pressure gauge PDX2 for measuring a pilot fuelgas differential pressure in front and on the back of the pilot fuelflow rate control valve 19. Moreover, the top hat fuel supply line 14 isprovided with a top hat fuel differential pressure gauge PDX3 formeasuring a top hat fuel gas differential pressure in front and on theback of the top hat fuel flow rate control valve 21.

As schematically shown in FIG. 3, the pilot manifold 23 is configured todistribute the pilot fuel gas, which is supplied through the pilot fuelsupply line 13, to the pilot nozzles 25 of the respective combustors 3.Although illustration is omitted therein, the main manifold 22 issimilarly configured to distribute the main fuel gas supplied throughthe main fuel supply line 12 to the main nozzles 26 of the respectivecombustors 3, and the top hat manifold 24 is also configured todistribute the top hat fuel gas supplied through the top hat fuel supplyline 14 to the top hat nozzles 27 of the respective combustors 3.

Meanwhile, the main fuel pressure control valve 16 is configured toadjust the main fuel gas differential pressure in front and on the backof the main fuel flow rate control valve 17, which is measured by themain fuel differential pressure gauge PDX1, to a constant value. Thepilot fuel pressure control valve 18 is configured to adjust the pilotfuel gas differential pressure in front and on the back of the pilotfuel flow rate control valve 19, which is measured by the pilot fueldifferential pressure gauge PDX2, to a constant value. Moreover, the tophat fuel pressure control valve 20 is configured to adjust the top hatfuel gas differential pressure in front and on the back of the top hatfuel flow rate control valve 21, which is measured by the top hat fueldifferential pressure gauge PDX3, to a constant value.

Further, the main fuel flow rate control valve 17 is configured toadjust a flow rate of the main fuel gas which is supplied to the mainnozzles 26 of all of the combustors 3 through the main fuel supply line12. The pilot fuel flow rate control valve 19 is configured to adjust aflow rate of the pilot fuel gas which is supplied to the pilot nozzles25 of all of the combustors 3 through the pilot fuel supply line 13.Moreover, the top hat fuel flow rate control valve 21 is configured toadjust a flow rate of the top hat fuel gas which is supplied to the tophat nozzles 27 of all of the combustors 3 through the top hat fuelsupply line 14.

Meanwhile, as shown in FIG. 1, the fuel supply line 11 is provided witha fuel stop valve 15 and a fuel gas thermometer Tf. The fuel gasthermometer Tf measures the temperature of the fuel gas flowing on thefuel gas supply line 11 and outputs a measurement signal in terms ofthis fuel gas temperature to a gas turbine combustion control device 41(see FIG. 4) fitted to this gas turbine 1, and the like. Measurementsignals from the main manifold pressure gauge PX1, the pilot manifoldpressure gauge PX2, the top hat manifold pressure gauge PX3, the mainfuel differential pressure gauge PDX1, the pilot fuel differentialpressure gauge PDX2, and the top hat fuel differential pressure gaugePDX3 are also outputted to the gas turbine combustion control device 41and the like.

Moreover, the power transmission system of the power generator 5 isprovided with a power meter PW. An intake-air thermometer Ta, anintake-air pressure gauge PX4, and an intake-air flowmeter FX1 areprovided on the inlet side of the compressor 4, while a cylinderpressure gauge PX5 is provided on the outlet side of the compressor 4.The turbine bypass line 9 is provided with a turbine bypass flowmeterFX2. The exhaust line 32 is provided with an exhaust gas thermometer Th.

The power meter PW measures generated power (the power generator output:the gas turbine output) of the power generator 5 and outputs ameasurement signal of this power generator output (the gas turbineoutput) to the gas turbine combustion control device 41 and the like.The intake-air thermometer Ta measures the intake-air temperature in thecompressor 4 (the temperature of the air flowing into the compressor 4)and outputs a measurement signal of this intake-air temperature to thegas turbine combustion control device 41 and the like. The intake-airpressure gauge PX4 measures the intake-air pressure of the compressor 4(the pressure of the air flowing into the compressor 4) and outputs ameasurement signal of this intake-air pressure to the gas turbinecombustion control device 41 and the like. The intake-air flowmeter FX1measures the flow rate of the intake air flowing into the compressor 4and outputs a measurement signal of this intake-air flow rate to the gasturbine combustion control device 41 and the like. The cylinder pressuregauge PX5 measures the cylinder pressure representing the pressure ofthe compressed air to be ejected from the compressor 4 and outputs ameasurement signal of this cylinder pressure to the gas turbinecombustion control device 41 and the like. The turbine bypass flowmeterFX2 measures the turbine bypass flow rate of the compressed air flowingthrough the turbine bypass line 9 and outputs a measurement signal ofthis turbine bypass flow rate to the gas turbine combustion controldevice 41 and the like. The exhaust gas thermometer Th measures thetemperature of the exhaust gas discharged from the gas turbine body 2and outputs a measurement signal of this exhaust gas temperature to thegas turbine combustion control device 41 and the like.

Next, the gas turbine combustion control device 41 will be describedwith reference to FIG. 4 to FIG. 33. Here, respective processingfunctions of the gas turbine combustion control device 41 areconstructed in the form of software (computer programs) that is executedby a computer. However, the present invention will not be limited onlyto this configuration. It is also possible to construct the processingfunctions in the form of hardware.

As shown in FIG. 4, a power generator output command value transmittedfrom an unillustrated central load dispatching center, and an IGVaperture command value transmitted from the unillustrated IGV controldevice are inputted to the gas turbine combustion control device 41.Here, the power generator output command value is not always required tobe transmitted from the central load dispatching center. For example,the power generator output command value may be set up by a powergenerator output setting device that is installed in the gas turbinepower generation facility. Moreover, the IGV aperture command value isadopted as the IGV aperture used for computation of a CLCSO (acombustion load command) in this case. However, the present inventionwill not be limited only to this configuration. For example, in the caseof measuring the IGV aperture, it is possible to use this measurementvalue instead.

In addition, the power generator output measured by the power meter PW,the intake-air temperature measured by the intake-air thermometer Ta,the fuel gas temperature measured by the fuel gas thermometer Tf, theexhaust gas temperature measured by the exhaust gas thermometer Th, theintake-air flow rate measured by the intake-air flowmeter FX1, theturbine bypass flow rate measured by the turbine bypass flowmeter FX2,the main manifold pressure measured by the main manifold pressure gaugePX1, the pilot manifold pressure measured by the pilot manifold pressuregauge PX2, the top hat manifold pressure measured by the top hatmanifold pressure gauge PX3, the intake-air pressure measured by theintake-air pressure gauge PX4, the cylinder pressure measured by thecylinder pressure gauge PX5, the main fuel gas differential pressuremeasured by the main fuel differential pressure gauge PDX1, the pilotfuel gas differential pressure measured by the pilot fuel differentialpressure gauge PDX2, and the top hat fuel gas differential pressuremeasured by the top hat fuel differential pressure gauge PDX3 areinputted as actual measured values to the gas turbine combustion controldevice 41.

Thereafter, based on these input signals and the like, the gas turbinecombustion control device 41 calculates a main fuel flow rate controlvalve position command value for performing main fuel gas flow ratecontrol, a pilot fuel flow rate control valve position command value forperforming pilot fuel gas flow rate control, a top hat fuel flow ratecontrol valve position command value for performing top hat fuel gasflow rate control, and a combustor bypass valve position command valuefor performing combustion bypassing flow rate control.

An outline of a process flow in the gas turbine combustion controldevice 41 will be described with reference to FIG. 5. Firstly, the CLCSOis computed based on the power generator output, the IGV aperturecommand value, the intake-air temperature, a turbine bypass ratio (theturbine bypass flow rate/the intake-air flow rate) representing a ratiobetween the intake-air flow rate and the turbine bypass flow rate, andan atmospheric pressure ratio (an atmospheric pressure/a standardatmospheric pressure) representing a ratio between the atmosphericpressure and the standard atmospheric pressure. This CLCSO is equivalentto a value obtained by rendering a combustion gas temperature at aninlet of a gas turbine (a temperature of the fuel gas at an inlet of thegas turbine body when the fuel gas flow from the combustor 3 to the gasturbine body 2) dimensionless. In other words, the CLCSO is a valueproportional to the combustion gas temperature at the inlet of the gasturbine. Thereafter, a pilot ratio representing a ratio of a pilot fuelgas flow rate (a weight flow rate) relative to a total fuel gas flowrate (a weight flow rate), a top hat ratio representing a ratio of a tophat fuel gas flow rate (a weight flow rate) relative to the total fuelgas flow rate (the weight flow rate), and a main ratio representing aratio of a main fuel gas flow rate (a weight flow rate) relative to thetotal fuel gas flow rate (the weight flow rate) are calculated based onthis CLCSO.

Subsequently, the respective weight flow rates, namely, the pilot fuelgas flow rate G_(fPL), the top hat fuel gas flow rate G_(fTH), and themain fuel gas flow rate G_(fMA) are calculated based on the pilot ratio,the top hat ratio, and the main ratio, respectively. Further, a Cv valueof the pilot fuel flow rate control valve 19, a Cv value of the top hatfuel flow rate control valve 21, and a Cv value of the main fuel flowrate control valve 17 are calculated based on the pilot fuel gas flowrate G_(fPL), the top hat fuel gas flow rate G_(fTH), and the main fuelgas flow rate G_(fMA), respectively. Then, the pilot fuel flow ratecontrol valve position command value, the top hat fuel flow rate controlvalve position command value, and the main fuel flow rate control valveposition command value based on the Cv value of the pilot fuel flow ratecontrol valve 19, the Cv value of the top hat fuel flow rate controlvalve 21, and the Cv value of the main fuel flow rate control valve 17,respectively. Meanwhile, in terms of the combustor bypass valve 8, thecombustor bypass valve position command value is calculated based on theCLCSO as well.

Next, the processing to be executed by the gas turbine combustioncontrol device 41 will be described in detail. In the following, theprocessing to calculate the CLCSO will be firstly described concerningthe processing of the gas turbine combustion control device 41. Then,the processing for calculating the respective valve position commandvalues based on this CLCSO will be described.

(Computation of CLCSO)

In order to formulate the pilot ratio, the top hat ratio, the mainratio, and the aperture of the combustor bypass valve into functions ofthe combustion gas temperature TIT at the inlet of the gas turbinerepresenting original concepts, the CLCSO formed by rendering thecombustion gas temperature TIT at the inlet of the gas turbinedimensionless is applied as a control parameter. For this reason, theCLCSO is computed to begin with. As shown in FIG. 6, the CLCSO isassumed to be proportional to the combustion gas temperature TIT at theinlet of the gas turbine (CLCSO∝TIT). Here, in the illustrated example,the CLCSO corresponding to the combustion gas temperature TIT at theinlet of the gas turbine of 700° C., which is defined as a firstcombustion gas temperature at the inlet of the gas turbine, is assumedto be 0%. Meanwhile, the CLCSO corresponding to the combustion gastemperature TIT at the inlet of the gas turbine of 1500° C., which isdefined as a second combustion gas temperature at the inlet of the gasturbine, is assumed to be 100%. It is to be noted that the firstcombustion gas temperature at the inlet of the gas turbine as well asthe second combustion gas temperature at the inlet of the gas turbineconstituting the criteria for computing the CLCSO are not limited onlyto the 700° C. and 1500° C. It is possible to set up other temperaturesas appropriate.

Moreover, a relation (a function) between the CLCSO and the pilot ratioas shown in FIG. 7 as an example, a relation (a function) between theCLCSO and the top hat ratio as shown in FIG. 8 as an example, and arelation (a function) between the CLCSO and the combustor bypass valveposition command value (BYCSO) as shown in FIG. 9 as an example are setup in advance. Relations of the combustion gas temperature TIT at theinlet of the gas turbine with the pilot ratio, the top hat ratio, andthe aperture of the combustor bypass valve can be obtained inpreliminary studies (in gas turbine designing processes). Accordingly,based on these relations, it is possible to set up the relations of theCLCSO with the pilot ratio, the top hat ratio, and the combustor bypassvalve position command value (BYCSO) as shown in FIG. 7 to FIG. 9 asexamples. Moreover, by calculating the pilot ratio, the top hat ratio,and the aperture of the combustor bypass valve by use of the computedCLCSO and the relations show in FIG. 7 to FIG. 9, the pilot ratio, thetop hat ratio, and the aperture of the combustor bypass valve areuniquely determined relative to the combustion gas temperature TIT atthe inlet of the gas turbine because the CLCSO is proportional to thecombustion gas temperature TIT at the inlet of the gas turbine(CLCSO∝TIT). That is, the pilot ratio, the top hat ratio, and theaperture of the combustion bypass valve become functions of the CLCSO(the combustion gas temperature TIT at the inlet of the gas turbine).Since the main ratio is calculated based on the pilot ratio and the tophat ratio (to be described later in detail), the main ratio also becomesa function of the CLCSO (the combustion gas temperature TIT at the inletof the gas turbine).

The CLCSO is computed based on the gas turbine output (the powergenerator output). Specifically, a relation between the combustion gastemperature TIT at the inlet of the gas turbine and the gas turbineoutput (the power generator output) in terms of various IGV apertures isshown in FIG. 10, and a relation between the intake-air temperature andthe gas turbine output (the power generator output) in terms of thevarious IGV apertures is shown in FIG. 11. As shown in FIG. 10 and FIG.11, in terms of the various IGV apertures, it is possible to treat thecombustion gas temperature TIT at the inlet of the gas turbine is in thelinear relation with the gas turbine output (the power generatoroutput). Therefore, the combustion gas temperature TIT at the inlet ofthe gas turbine, i.e. the CLCSO is derived from the gas turbine output(the power generator output).

For this reason, a relation (a function) between the power generatoroutput (the gas turbine output) and the CLCSO is set up whileconsidering the IGV apertures and the intake-air temperatures shown inFIG. 12 and also considering the turbine bypass ratio and theatmospheric pressure (air pressure/standard atmospheric pressure: anaverage atmospheric pressure in a place where the gas turbine isinstalled is used as the standard atmospheric pressure, for example).

Specifically, a 700° C. MW value representing the power generator output(the gas turbine output) when the combustion gas temperature TIT at theinlet of the gas turbine is equal to 700° C. that is determined as thefirst combustion gas temperature at the inlet of the gas turbine, and a1500° C. MW value representing the power generator output (the gasturbine output) when the combustion gas temperature TIT at the inlet ofthe gas turbine is equal to 1500° C. that is determined as the secondcombustion gas temperature at the inlet of the gas turbine are set up inthe first place. Here, the temperature of 1500° C. is a maximumcombustion gas temperature (an upper limit) determined in the gasturbine designing processes in terms of durability of the combustor 3and the gas turbine body 2. Since the temperature is adjusted not toexceed this value, the temperature of 1500° C. is also referred to as atemperature controlled MW. These temperatures of 700° C. and 1500° C.(the temperature controlled MW) can be calculated in the preliminarystudies (in the gas turbine designing processes).

Then, as shown in FIG. 12, the CLCSO relative to the 700° C. MW isdefined as 0% and the CLCSO relative to the 1500° C. MW value is definedas 100%. It is to be noted, however, that the 700° C. MW value and the1500° C. MW value are the values considering the IGV aperture, theintake-air temperature, the turbine bypass ratio, and the atmosphericpressure ratio. That is, these values respectively represent the powergenerator output (the gas turbine output) at the combustion gastemperature TIT at the inlet of the gas turbine of 700° C. and the powergenerator output (the gas turbine output) at the combustion gastemperature TIT at the inlet of the gas turbine of 1500° C. in terms ofa certain IGV aperture, a certain intake-air temperature, a certainturbine bypass ratio, and a certain pressure ratio.

In other words, as shown in FIG. 13 as an example, the relation betweenthe power generator output (the gas turbine output) and the CLCSO variesdepending on the IGV aperture (such as 0% (when an intake-air passage isnot completely closed), 50% or 100%). As shown in FIG. 14 as an example,the relation between the power generator output (the gas turbine output)and the CLCSO also varies depending on the intake-air temperature (suchas −10° C. and 40° C.). Moreover, as shown in FIG. 15 as an example, therelation between the power generator output (the gas turbine output) andthe CLCSO also varies depending on the turbine bypass ratio. Althoughillustration is omitted herein, the relation between the power generatoroutput (the gas turbine output) and the CLCSO also varies depending onthe atmospheric pressure ratio (such as 1.0 or 1.1).

For this reason, the 1500° C. MW values corresponding to the IGVaperture, the intake-air temperature, the turbine bypass ratio, and theatmospheric pressure are set up in advance. Table 1 shown belowexemplifies the preset 1500° C. MW values corresponding to the IGVaperture, the intake-air temperature, the turbine bypass ratio, and theatmospheric pressure ratio. The example shown in Table 1 sets up the1500° C. MW values in the cases where the IGV aperture is equal to anyone of 0%, 50%, and 100%, the intake-air temperature is equal to any oneof −10° C. and 40° C., and the turbine bypass ratio is equal to 10%.These values are obtained in the preliminary studies (in the gas turbinedesigning processes). Here, the 1500° C. MW value in the case where theturbine bypass ratio is equal to 0% is solely determined by the IGVaperture and the intake-air temperature. For example, the 1500° C. MWvalue is equal to 140 MW when the IGV aperture (the IGV aperturecommand) is equal to 100%, the intake-air aperture is equal to −10° C.,and the turbine bypass ratio is equal to 0%, while the 1500° C. MW valueis equal to 110 MW when the IGV aperture is equal to 100%, theintake-air aperture is equal to −10° C., and the turbine bypass ratio isequal to 10%.

TABLE 1 When TIT = 1500° C. (1500° C. MW) IGV aperture 0% 50% 100%Intake-air −10° C. 100 MW 120 MW 140 MW temperature (70 MW at (90 MW at(110 MW turbine turbine at turbine bypass bypass bypass ratio ratioratio equal to equal to equal to 10%) 10%) 10%)  40° C. 80 MW 100 MW 120MW (50 MW at (70 MW at (90 MW at turbine turbine turbine bypass bypassbypass ratio ratio ratio equal to equal to equal to 10%) 10%) 10%)

If any values of the IGV aperture, the intake-air temperature, and theturbine bypass ratio is different from those shown in Table 1 (when theIGV aperture is equal to 60%, the intake-air temperature is equal to 10°C., and the turbine bypass ratio is equal to 5%, for example), the 1500°C. MW value corresponding to the IGV aperture, the intake-airtemperature, and the turbine bypass ratio can be computed by linearinterpolation (interpolating calculation) by use of any of the 1500° C.MW values shown in Table 1.

Moreover, by multiplying the 1500° C. MW value considering the IGVaperture, the intake-air temperature, and the turbine bypass ratio bythe atmospheric pressure ratio, it is possible to compute the 1500° C.MW value while considering the atmospheric pressure ratio as well.

Although detailed explanation will be omitted herein, it is alsopossible to calculate the value considering the IGV aperture, theintake-air temperature, the turbine bypass ratio, and the atmosphericpressure ratio in a similar manner to the case of 1500° C. MW value.Table 2 shown below exemplifies the preset 700° C. MW valuescorresponding to the IGV aperture, the intake-air temperature, theturbine bypass ratio, and the atmospheric pressure ratio.

TABLE 2 When TIT = 700° C. (700° C. MW) IGV aperture 0% 50% 100%Intake-air −10° C. 5 MW 6 MW 7 MW temperature (3 MW at (4 MW at (5 MW atturbine turbine turbine bypass bypass bypass ratio ratio ratio equal toequal to equal to 10%) 10%) 10%)  40° C. 3 MW 4 MW 5 MW (1 MW at (2 MWat (3 MW at turbine turbine turbine bypass bypass bypass ratio ratioratio equal to equal to equal to 10%) 10%) 10%)

Then, upon determination of the 700° C. MW and 1500° C. MW values whileconsidering the IGV aperture, the intake-air temperature, the turbinebypass ratio, and the atmospheric pressure ratio, the CLCSO is computedin accordance with the following formula (1) representing the directinterpolation (interpolating calculation) formula based on the 700° C.MW and 1500° C. MW values and an actual measurement value of the gasturbine output (the power generator output):

$\begin{matrix}{{{CLCSO}(\%)} = {\frac{\begin{matrix}{{{Actual}\mspace{14mu}{value}\mspace{14mu}{of}\mspace{14mu}{gas}\mspace{14mu}{turbine}\mspace{14mu}{output}\mspace{11mu}({MW})} -} \\{700\;{{^\circ}CMW}}\end{matrix}}{{1500{{^\circ}CMW}} - {700{{^\circ}CMW}}} \times 100}} & (1)\end{matrix}$

Now, an explanation will be made based on computation logic of the CLCSO(combustion load command computing means) shown in FIG. 16. First, afunction generator 51 as second gas turbine output computing meanscomputes the 1500° C. MW value (the temperature controlled MW) as asecond gas turbine output based on an actual measurement value of theintake-air temperature, the IGV aperture command value, and the turbinebypass ratio (a turbine bypass flow rate/intake-air flow rate)calculated by dividing an actual measurement value of a turbine bypassflow rate by an actual measurement value of an intake-air flow rate(corresponding to a total amount of the compressed air) with a divider53. That is, the 1500° C. MW value is calculated while considering theIGV aperture, the intake-air temperature, and the turbine bypass ratio.The method of computing this 1500° C. MW value has been describedpreviously.

A function generator 52 as first gas turbine output computing meanscomputes the 700° C. MW value as a first gas turbine output based on theintake-air temperature, the IGV aperture command value, and the turbinebypass ratio. That is, the 700° C. MW value is calculated whileconsidering the IGV aperture, the intake-air temperature, and theturbine bypass ratio. The method of computing this 700° C. MW value issimilar to the case of computing the 1500° C. MW value.

A divider 54 calculates the atmospheric pressure ratio (intake-airpressure/standard atmospheric pressure) by dividing an actualmeasurement value of an intake-air pressure (the atmospheric pressure)by the standard atmospheric pressure set up with a signal generator 61.A multiplier 55 multiplies the 1500° C. MW value calculated with thefunction generator 51 by the atmospheric pressure ratio calculated withthe divider 54, to calculate the 1500° C. MW value in consideration ofthe atmospheric pressure ratio as well. The 1500° C. MW value calculatedwith the multiplier 55 is outputted to a subtracter 57 through alearning circuit 62 functioning as learning means. Details of theleaning circuit 62 will be described later. A multiplier 56 multipliesthe 700° C. MW value calculated with the function generator 52 by theatmospheric pressure ratio calculated with the divider 54 to calculatethe 700° C. MW value in consideration of the atmospheric pressure ratioas well.

The subtracter 57 subtracts the 700° C. MW value calculated with themultiplier 56 from the 1500° C. MW value calculated with the multiplier55 (or corrected by the learning circuit 62) (1500° C. MW−700° C. MW:see the formula (1)). A subtracter 58 subtracts the 700° C. MW valuecalculated with the multiplier 56 from the actual measurement value ofthe power generator output (the gas turbine output) (the actualmeasurement value of the power generator output (the gas turbine output)700° C. MW: see the formula (1)).

Thereafter, a divider 59 divides a result of subtraction with thesubtracter 58 by a result of subtraction with the subtracter 57 (see theformula (1)). In this way, it is possible to compute the CLCSO. Here, toexpress the CLCSO in percentage, an output value from the divider 59should be multiplied by 100. A rate setter 60 outputs an inputted valuefrom the divider 59 while restricting the value to a given rate ofchange instead of directly outputting the inputted value as the CLCSO inorder to avoid the main fuel flow rate control valve 17 and the likefrom frequently repeating opening and closing operations caused by asmall variation in the CLCSO attributable to a small variation in thegas turbine output (the power generator output) or the like.

Incidentally, when the gas turbine 1 is operated for a long period,deterioration in the performance of the gas turbine 1 may be caused bydeterioration in a compression performance of the compressor 4 and thelike. As a consequence, the power generator output (the gas turbineoutput) starts declining. That is, in this case, the power generatoroutput (the gas turbine output) does not reach the given (such as arated) power generator output (gas turbine output) as shown in FIG. 10even when the combustion gas temperature TIT at the inlet of the gasturbine reaches 1500° C. As a result, the CLCSO may also decline and therelation between the CLCSO and the combustion gas temperature TIT at theinlet of the gas turbine may be deviated. Accordingly, the relations ofthe combustion gas temperature TIT at the inlet of the gas turbine withthe pilot ratio, the top hat ratio, the main ratio, and the aperture ofthe combustor bypass valve will be also deviated. Therefore, it isnecessary to reduce the value of 1500° C. MW (the temperature controlledMW) for computing the CLCSO as well.

For this reason, in the gas turbine combustion control device 41, thecomputation logic of the CLCSO also includes the learning circuit 62 for1500° C. MW value (the temperature controlled MW) as shown in FIG. 17.

The learning circuit 62 firstly judges whether or not the combustion gastemperature TIT at the inlet of the gas turbine reaches the maximumcombustion gas temperature (1500° C.) before starting to learn the 1500°C. MW value (the temperature controlled MW) in order to judge whether ornot a decline in the power generator output (the gas turbine output) isattributable to deterioration in characteristics of the gas turbine 1.Specifically, when the combustion gas temperature TIT at the inlet ofthe gas turbine is equal to the maximum combustion gas temperature(1500° C.), there is a relation between a pressure ratio of thecompressor 4 (a ratio between a pressure on an inlet side and a pressureon an outlet side of the compressor 4) and the exhaust gas temperatureas shown in FIG. 18. Therefore, the learning circuit 62 monitors apressure ratio (the cylinder pressure/the intake-air pressure) of thecompressor 4 obtained from the actual measurement value of theintake-air pressure and the actual measurement value of the cylinderpressure as well as the actual measurement value of the exhaust gastemperature. Moreover, the learning circuit 62 judges that thecombustion gas temperature TIT at the inlet of the gas turbine reachesthe maximum combustion gas temperature (1500° C.) when the pressureratio and the exhaust gas temperature satisfy the relation shown in FIG.18, and then starts learning.

In this case, the learning circuit 62 firstly calculates a deviation(the power generator output−1500° C.) between the 1500° C. MW value (thetemperature controlled MW) after correction in terms of the atmosphericpressure to be inputted from the multiplier 55 in the computation logicof the CLCSO shown in FIG. 16 and the actual measurement value of thegas turbine output (the power generator output) by use of a subtracter(a deviation operator) 63. A PI (proportion and integration) controller64 calculates a correction coefficient by subjecting the deviationcalculated with the subtracter (the deviation operator) 63 toproportional and integral operations. A LOW limiter 65 limits thecorrection coefficient (ranging from 0 to 1) operated with the PIoperator 64 to a range from 0.95 to 1. The reason for providing thelimited range of the correction coefficient as described above is toconsider an amount of presumable reduction in the power generator output(the gas turbine output) by normal deterioration in the performance ofthe gas turbine 1 and to prevent excessive correction attributable to anabnormal drop of the output from the gas turbine 1. A multiplier 66multiplies the correction coefficient by the 1500° C. MW value (thetemperature controlled MW) inputted from the multiplier 55, and outputsa result of multiplication to the subtracter (the deviation operator)63.

By performing the processing as described above, the 1500° C. MW value(the temperature controlled MW) is corrected so as to coincide with theactual measurement value of the gas turbine output (the power generatoroutput). Then, the 1500° C. MW value (the temperature controlled MW)after correction is outputted to the subtracter 57 in the computationlogic of the CLCSO shown in FIG. 16 for use in the calculation of theCLCSO. Here, a lower value selector 67 selects a lower value out of the1500° C. MW value (the temperature controlled MW) after correction andthe rated power generator output (the gas turbine output) set up in asignal generator 68, and outputs the selected value for monitor displayand the like.

(Computation of Respective Valve Position Command Values Based on CLCSO)

Next, the processing for calculating the respective valve positioncommand values based on the CLCSO will be described.

First, computation logic of the combustor bypass valve position commandvalue (the BYCSO) will be described with reference to FIG. 19. Afunction generator 71 calculates the BYCSO corresponding to the CLCSOcalculated in accordance with the computation logic of the CLCSO basedon the preset function of the CLCSO and the combustor bypass valveposition command value (the BYCSO) as shown in FIG. 9.

Meanwhile, in this computation logic, this combustor bypass valveposition command value is subjected to correction based on the CLCSO andcorrection based on the intake-air temperature. Specifically, a functiongenerator 72 calculates a weight value of correction corresponding tothe CLCSO calculated in accordance with the computation logic of theCLCSO based on a function of the CLCSO and the weight of correction asshown in FIG. 20, which is set up in the preliminary studies (the gasturbine designing processes). A function generator 73 calculates acorrection efficient corresponding to the actual measurement value ofthe intake-air temperature based on a function of the intake-airtemperature and the correction coefficient as shown in FIG. 21, which isset up in the preliminary studies (the gas turbine designing processes).A multiplier 74 calculates an intake-air temperature correction amountby multiplying the weight value of correction based on the CLCSOcalculated with the function generator 72 by the correction coefficientbased on the intake-air temperature calculated with the functiongenerator 73. A subtracter 75 performs the intake-air temperaturecorrection of the BYCSO by subtracting the intake-air temperaturecorrection amount calculated with the multiplier 74 from the BYCSOcalculated with the function generator 71. That is, the functiongenerators 72 and 73, the multiplier 74, and the subtracter 75collectively constitute intake-air temperature correcting means.

The reason for performing the correction of the BYSCO based on theintake-air temperature is to achieve more appropriate combustion controlrelative to the variation in the intake-air temperature as compared tothe case of determining the BYSCO simply based on the CLCSO (thecombustion gas temperature at the inlet of the gas turbine). Here, theintake-air temperature correction amount may be set to a relativelylarge value with respect to the BYCSO without causing any problems atthe time of a low load (a low gas turbine output). However, a smallchange in the BYCSO may cause a large change in a combustion state atthe time of a high load (a high gas turbine output). Accordingly, it isnecessary to reduce the intake-air temperature correction amountrelative to the BYCSO. For this reason, the weight of correction isdetermined in response to the CLCSO (i.e. the gas turbine output) asdescribed above, and the appropriate intake-air temperature correctionamount for the BYCSO corresponding to the CLCSO is determined bymultiplying this weight value by the correction coefficient which isobtained from the intake-air temperature.

Thereafter, the gas turbine combustion control device 41 controls thebypassing flow rate of the compressed air relative to the combustor 3 byregulating the aperture of the combustor bypass valve 8 based on theCLCSO calculated in accordance with this computation logic.

Next, computation logic (fuel flow rate command setting means) of apilot fuel flow rate command value (PLCSO) will be described withreference to FIG. 22. A function generator 81 calculates the pilot ratiocorresponding to the CLCSO calculated in accordance with the computationlogic of the CLCSO based on the function of the CLCSO and the pilotratio which is set up in advance as shown in FIG. 7.

Meanwhile, in this computation logic as well, this pilot ratio issubjected to correction based on the CLCSO and correction based on theintake-air temperature. Specifically, a function generator 82 calculatesa weight value of correction corresponding to the CLCSO calculated inaccordance with the computation logic of the CLCSO based on the functionof the CLCSO and the weight of correction as shown in FIG. 20, which isset up in the preliminary studies (the gas turbine designing processes).A function generator 83 calculates a correction efficient correspondingto the actual measurement value of the intake-air temperature based onthe function of the intake-air temperature and the correctioncoefficient as shown in FIG. 21, which is set up in the preliminarystudies (the gas turbine designing processes). A multiplier 84calculates an intake-air temperature correction amount by multiplyingthe weight value of correction based on the CLCSO calculated with thefunction generator 82 by the correction coefficient based on theintake-air temperature calculated with the function generator 83. Asubtracter 85 performs the intake-air temperature correction of thepilot ratio by subtracting the intake-air temperature correction amountcalculated with the multiplier 84 from the pilot ratio calculated withthe function generator 81. That is, the function generators 82 and 83,the multiplier 84, and the subtracter 85 collectively constitute theintake-air temperature correcting means.

The reason for performing the correction of the pilot ratio based on theintake-air temperature is to achieve more appropriate combustion controlrelative to the variation in the intake-air temperature as compared tothe case of determining the pilot ratio simply based on the CLCSO (thecombustion gas temperature at the inlet of the gas turbine). Here, theintake-air temperature correction amount may be set to a relativelylarge value with respect to the pilot ratio without causing any problemsat the time of the low load (the low gas turbine output). However, asmall change in the pilot ratio may cause a large change in thecombustion state at the time of the high load (i.e. the high gas turbineoutput). Accordingly, it is necessary to reduce the intake-airtemperature correction amount relative to the pilot ratio. For thisreason, the weight of correction is determined in response to the CLCSO(i.e. the gas turbine output) as described above, and the appropriateintake-air temperature correction amount for the pilot ratiocorresponding to the CLCSO is determined by multiplying this weightvalue by the correction coefficient which is obtained from theintake-air temperature.

Thereafter, a multiplier 86 computes the PLCSO by multiplying a totalfuel flow rate command value (CSO) by the pilot ratio calculated withthe subtracter 85. The total fuel flow rate command value (CSO) is avalue proportional to a total fuel gas flow rate (a weight flow rate)G_(f) to be supplied to the combustor 3 (CSO∝G_(f)). Therefore, thePLCSO is a value proportional to the pilot gas fuel flow rate G_(fPL).

Here, the total fuel flow rate command value (CSO) is set up based on arelation between a power generator output command value, which is set upin advance in the preliminary studies (the gas turbine designingprocesses), and the CSO (i.e. the total fuel gas flow rate G_(f).Specifically, the gas turbine combustion control device 41 sets up thetotal fuel flow rate command value (CSO) based on the preset relation(the function) between the power generator output command value and theCSO by use of the power generator output command value set up by thecentral load dispatching center or the like. Here, the gas turbinecombustion control device 41 adjusts the total fuel flow rate commandvalue (CSO) by use of an unillustrated control unit such that the actualmeasurement value of the power generator output coincides with the powergenerator output command value. For example, the total fuel flow ratecommand value (CSO) is adjusted such that the actual measurement valueof the power generator output coincides with the power generator outputcommand value by subjecting a deviation between the actual measurementvalue of the power generator output and the power generator outputcommand value to proportional and integral operations with a PIcontroller.

Next, computation logic (the fuel flow rate command setting means) of atop hat fuel flow rate command value (THCSO) will be described withreference to FIG. 23. A function generator 91 calculates the top hatratio corresponding to the CLCSO calculated in accordance with thecomputation logic of the CLCSO based on the function of the CLCSO andthe top hat ratio which is set up in advance as shown in FIG. 8.

Meanwhile, in this computation logic as well, this top hat ratio issubjected to correction based on the CLCSO and correction based on theintake-air temperature. Specifically, a function generator 92 calculatesa weight value of correction corresponding to the CLCSO calculated inaccordance with the computation logic of the CLCSO based on the functionof the CLCSO and the weight of correction as shown in FIG. 20, which isset up in the preliminary studies (the gas turbine designing processes).A function generator 93 calculates a correction efficient correspondingto the actual measurement value of the intake-air temperature based onthe function of the intake-air temperature and the correctioncoefficient as shown in FIG. 21, which is set up in the preliminarystudies (the gas turbine designing processes). A multiplier 94calculates an intake-air temperature correction amount by multiplyingthe weight value of correction based on the CLCSO calculated with thefunction generator 92 by the correction coefficient based on theintake-air temperature calculated with the function generator 93. Asubtracter 95 performs the intake-air temperature correction of the tophat ratio by subtracting the intake-air temperature correction amountcalculated with the multiplier 94 from the top hat ratio calculated withthe function generator 91. That is, the function generators 92 and 93,the multiplier 94, and the subtracter 95 collectively constitute theintake-air temperature correcting means.

The reason for performing the correction of the top hat ratio based onthe intake-air temperature is to achieve more appropriate combustioncontrol relative to the variation in the intake-air temperature ascompared to the case of determining the top hat ratio simply based onthe CLCSO (the combustion gas temperature at the inlet of the gasturbine). Here, the intake-air temperature correction amount may be setto a relatively large value with respect to the top hat ratio withoutcausing any problems at the time of the low load (the low gas turbineoutput). However, a small change in the top hat ratio may cause a largechange in the combustion state at the time of the high load (the highgas turbine output). Accordingly, it is necessary to reduce theintake-air temperature correction amount relative to the top hat ratio.For this reason, the weight of correction is determined in response tothe CLCSO (i.e. the gas turbine output) as described above, and theappropriate intake-air temperature correction amount for the top hatratio corresponding to the CLCSO is determined by multiplying thisweight value by the correction coefficient which is obtained from theintake-air temperature. Although details will be described later, themain ratio is also computed based on the pilot ratio and the top hatratio, and is therefore subjected to intake-air temperature correction.

A multiplier 96 computes the THCSO by multiplying the CSO by the top hatratio calculated with the subtracter 95. The THCSO is proportional tothe top hat gas fuel flow rate (a weight flow rate) G_(fTH).

Next, computation logic of the respective flow rate control valveposition command values will be described with reference to FIG. 24.

First, the computation logic of the pilot fuel flow rate control valvecommand value will be described. A function generator 101 computes thevalue of the pilot fuel flow rate G_(fPL) corresponding to the PLCSOcalculated with the multiplier 86 in accordance with the computationlogic of the PLCSO as described above based on a function of the PLCSOand the pilot gas flow rate G_(fPL) as shown in FIG. 25 as an example(fuel flow rate setting means). In other words, the PLCSO is convertedinto a weight flow rate Q. The function of (or a proportional relationbetween) the PLCSO and the pilot fuel gas flow rate G_(fPL) is set up inadvance in the preliminary studies (the gas turbine designingprocesses).

Subsequently, the Cv value of the pilot fuel flow rate control valve 19is computed based on the following formula (2) representing a Cv valuecalculation formula:

$\begin{matrix} \begin{matrix}{{Cv} = {\frac{aG}{289}\sqrt{\frac{\gamma( {t + 273} )}{P_{1}^{2} - P_{2}^{2}}}}} \\{a = {\frac{1}{\gamma_{N}} \cdot \frac{273 + 15.6}{273}}}\end{matrix} \} & (2)\end{matrix}$

In the formula (2), reference code t denotes the temperature of thepilot fuel gas flowing on the pilot fuel flow rate control valve 19. Avalue measured with the fuel gas thermometer Tf is applied to this pilotfuel gas temperature. Reference code γ denotes a gas density ratiorelative to the air, which is a preset value. Reference code G denotesthe pilot fuel gas flow rate (the weight flow rate) flowing on the pilotfuel flow rate control valve 19. The pilot fuel gas flow rate G_(fPL)calculated with the function generator 101 is applied to this pilot fuelgas flow rate. Reference code a denotes a coefficient used forconverting the pilot fuel gas flow rate G into a volume flow rate (m³/h)at 15.6° C. and at 1 ata. The coefficient a is a preset value. Referencecode γ_(N) denotes gas density in a normal state.

Moreover, in the formula (2), reference code P₂ denotes a back pressure(a pressure on a downstream side) of the pilot fuel flow rate controlvalve 19. A measurement value or a corrected value (to be describedlater in detail) of the pilot manifold pressure gauge PX2 is applied tothis back pressure. Reference code P₁ denotes a front pressure (apressure on an upstream side) of the pilot fuel flow rate control valve19. A value obtained by adding a front-to-back differential pressure ofthe pilot fuel flow rate control valve 19 (such as 4 kg/cm²) to themeasurement value of the pilot manifold pressure gauge PX2 is applied tothis front pressure. This front-to-back differential pressure isadjusted to be a constant value by use of the pilot fuel pressurecontrol valve 18. It is to be noted, however, that the present inventionwill not be limited only to this configuration. It is possible to applya measurement value of the pilot fuel differential pressure gauge PDX2to the front-to-back differential pressure. Alternatively, when thefront pressure of the pilot fuel flow rate control valve 19 is measuredwith a pressure gauge, it is possible to apply the measurement value ofthat pressure gauge to the P₁ value.

In terms of explanation based on the computation logic, a functiongenerator 102 performs a calculation in accordance with the followingformula (3) based on the pilot manifold pressure (used as the backpressure P₂), which is either the actual measurement value or thecorrected value using manifold pressure correction logic 130 (to bedescribed later in detail) functioning as pressure correcting means:

$\begin{matrix}\frac{1}{\sqrt{( {4 + P_{2}} )^{2} - P_{2}^{2}}} & (3)\end{matrix}$

A function generator 103 performs a calculation in accordance with thefollowing formula (4) based on the fuel gas temperature (used as thepilot fuel gas temperature t), which is either an actual measurementvalue inputted by use of fuel gas temperature correction logic 120 (tobe described later in detail) functioning as fuel temperature correctingmeans, or a constant value:

$\begin{matrix}\frac{a\sqrt{\gamma( {t + 273} )}}{289} & (4)\end{matrix}$

A multiplier 104 multiplies the pilot fuel gas flow rate G_(fPL) (usedas the pilot fuel gas flow rate G) calculated with the functiongenerator 101 by a result of calculation with the function generator102, and then by a result of calculation with the function generator103. In this way, the calculation of the above-described formula (2) iscompleted and the Cv value of the pilot fuel flow rate control valve 19is obtained (Cv value setting means). A function generator 105calculates an aperture of the pilot fuel flow rate control valvecorresponding to the Cv value of the pilot fuel flow rate control valve19 calculated with the multiplier 104 based on a function of theaperture of the pilot fuel flow rate control valve and the Cv value asshown in FIG. 26, which is set up in advance in the preliminary studies(specifications of the control valve). Then, the aperture of the pilotfuel flow rate control valve is outputted as the pilot fuel flow ratecontrol valve position command value (fuel flow rate control valveposition command setting means).

Thereafter, the gas turbine combustion control device 41 controls thepilot fuel gas flow rate by regulating the aperture of the pilot fuelflow rate control valve 19 based on the pilot fuel flow rate controlvalve position command value calculated in accordance with thiscomputation logic.

Now, the computation logic of the top hat fuel flow rate control valvecommand value will be described. A function generator 106 computes thevalue of the top hat fuel gas flow rate G_(fTH) corresponding to theTHCSO calculated with the multiplier 96 in accordance with thecomputation logic of the THCSO as described above based on a function ofthe THCSO and the top hat fuel gas flow rate G_(fTH) as shown in FIG. 27as an example (the fuel flow rate setting means). In other words, theTHCSO is converted into a weight flow rate Q. The function of (or aproportional relation between) the THCSO and the top hat fuel gas flowrate G_(fTH) is set up in advance in the. preliminary studies (the gasturbine designing processes).

Subsequently, the Cv value of the top hat fuel flow rate control valve21 is computed based on the above-described formula (2) (the Cv valuecalculation formula). In terms of the formula (2) in this case, however,it is to be noted that the reference code t denotes the temperature ofthe top hat fuel gas flowing on the top hat fuel flow rate control valve21. The value measured with the fuel gas thermometer Tf is applied tothis top hat fuel gas temperature. The reference code G denotes the tophat fuel gas flow rate (the weight flow rate) flowing on the top hatfuel flow rate control valve 21. The top hat fuel gas flow rate G_(fTH)calculated with the function generator 106 is applied to this top hatfuel gas flow rate. The reference code a denotes a coefficient used forconverting the top hat fuel gas flow rate G into a volume flow rate(m³/h) at 15.6° C. and at 1 ata.

Moreover, in the formula (2), the reference code P₂ denotes a backpressure (a pressure on a downstream side) of the top hat fuel flow ratecontrol valve 21. A measurement value or a corrected value (to bedescribed later in detail) of the top hat manifold pressure gauge PX3 isapplied to this back pressure. The reference code P₁ denotes a frontpressure (a pressure on an upstream side) of the top hat fuel flow ratecontrol valve 21. A value obtained by adding a front-to-backdifferential pressure of the top hat fuel flow rate control valve 21(such as 4 kg/cm²) to the measurement value of the top hat manifoldpressure gauge PX3 is applied to this front pressure. This front-to-backdifferential pressure is adjusted to be a constant value by use of thetop hat fuel pressure control valve 20. It is to be noted, however, thatthe present invention will not be limited only to this configuration. Itis possible to apply a measurement value of the top hat fueldifferential pressure gauge PDX3 to the differential pressure.Alternatively, when the front pressure of the top hat fuel flow ratecontrol valve 21 is measured with a pressure gauge, it is possible toapply the measurement value of that pressure gauge to the P₁ value.

In terms of explanation based on the computation logic, a functiongenerator 107 performs the calculation in accordance with theabove-described formula (3) based on the top hat manifold pressure (usedas the back pressure P₂), which is either the actual measurement valueor the corrected value using manifold pressure correction logic 140 (tobe described later in detail) functioning as the pressure correctingmeans. The function generator 103 performs the calculation in accordancewith the above-described formula (4) based on an actual measurementvalue of the fuel gas temperature (used as the top hat fuel gastemperature t) (as similar to the case of calculating the Cv value ofthe pilot fuel flow rate control valve 19).

A multiplier 109 multiplies the top hat fuel gas flow rate G_(fTH) (usedas the top hat fuel gas flow rate G) calculated with the functiongenerator 106 by a result of calculation with the function generator107, and then by a result of calculation with the function generator103. In this way, the calculation of the above-described formula (2) iscompleted and the Cv value of the top hat fuel flow rate control valve21 is obtained (the Cv value setting means). A function generator 110calculates an aperture of the top hat fuel flow rate control valvecorresponding to the Cv value of the top hat fuel flow rate controlvalve 21 calculated with the multiplier 109 based on the function of theaperture of the top hat fuel flow rate control valve and the Cv value asshown in FIG. 26, which is set up in advance in the preliminary studies(the specifications of the control valve). Then, the aperture of the tophat fuel flow rate control valve is outputted as the top hat fuel flowrate control valve position command value (the fuel flow rate controlvalve position command setting means).

Thereafter, the gas turbine combustion control device 41 controls thetop hat fuel gas flow rate by regulating the aperture of the top hatfuel flow rate control valve 21 based on the top hat fuel flow ratecontrol valve position command value calculated in accordance with thiscomputation logic.

Now, the computation logic of the main fuel flow rate control valvecommand value will be described. An adder 111 adds the PLCSO calculatedwith the multiplier 86 of the computation logic of the PLCSO to theTHCSO calculated with the multiplier 96 of the computation logic of theTHCSO (PLCSO+THCSO). A subtracter 112 subtracts a result of additionwith the adder 111 from the CSO (MACSO=CSO−PLCSO−THCSO) and therebycomputes a main fuel flow rate command value (MACSO) (the fuel flow ratecommand setting means). The MACSO is proportional to the main fuel gasflow rate G_(fMA).

A function generator 113 computes the value of the main fuel gas flowrate G_(fMA) corresponding to the MACSO calculated with the subtracter112 based on a function of the MACSO and the main fuel gas flow rateG_(fMA) as shown in FIG. 28 as an example (the fuel flow rate settingmeans). In other words, the MACSO is converted into a weight flow rateQ. The function of (or a proportional relation between) the MACSO andthe main fuel gas flow rate G_(fMA) is set up in advance in thepreliminary studies (the gas turbine designing processes).

Subsequently, the Cv value of the main fuel flow rate control valve 17is computed based on the above-described formula (2) (the Cv valuecalculation formula). In terms of the formula (2) in this case, however,it is to be noted that the reference code t denotes the temperature ofthe main fuel gas flowing on the main fuel flow rate control valve 17.The value measured with the fuel gas thermometer Tf is applied to thismain fuel gas temperature. The reference code G denotes the main fuelgas flow rate (the weight flow rate) flowing on the main fuel flow ratecontrol valve 17. The main fuel gas flow rate G_(fMA) calculated withthe function generator 113 is applied to this main fuel gas flow rate.The reference code a denotes a coefficient used for converting the mainfuel gas flow rate G into a volume flow rate (m³/h) at 15.6° C. and at 1ata.

Moreover, in the formula (2), the reference code P₂ denotes a backpressure (a pressure on a downstream side) of the main fuel flow ratecontrol valve 17. A measurement value or a corrected value (to bedescribed later in detail) of the main manifold pressure gauge PX1 isapplied to this back pressure. The reference code P₁ denotes a frontpressure (a pressure on an upstream side) of the main fuel flow ratecontrol valve 17. A value obtained by adding a front-to-backdifferential pressure of the main fuel flow rate control valve 17 (suchas 4 kg/cm²) to the measurement value of the main manifold pressuregauge PX1 is applied to this front pressure. This front-to-backdifferential pressure is adjusted to be a constant value by use of themain fuel pressure control valve 16. It is to be noted, however, thatthe present invention will not be limited only to this configuration. Itis possible to apply a measurement value of the main fuel differentialpressure gauge PDX1 to the front-to-back differential pressure.Alternatively, when the front pressure of the main fuel flow ratecontrol valve 17 is measured with a pressure gauge, it is possible toapply the measurement value of that pressure gauge to the P₁ value.

In terms of explanation based on the computation logic, a functiongenerator 114 performs the calculation in accordance with theabove-described formula (3) based on the main manifold pressure (used asthe back pressure P₂), which is either the actual measurement value orthe corrected value using manifold pressure correction logic 150 (to bedescribed later in detail) functioning as the pressure correcting means.The function generator 103 performs the calculation in accordance withthe above-described formula (4) based on an actual measurement value ofthe fuel gas temperature (used as the main fuel gas temperature t) (assimilar to the case of calculating the Cv value of the pilot fuel flowrate control valve 19).

A multiplier 115 multiplies the main fuel gas flow rate G_(fMA) (used asthe main fuel gas flow rate G) calculated with the function generator113 by a result of calculation with the function generator 114, and thenby a result of calculation with the function generator 103. In this way,the calculation of the above-described formula (2) is completed and theCv value of the main fuel flow rate control valve 17 is obtained (the Cvvalue setting means). A function generator 116 calculates an aperture ofthe main fuel flow rate control valve corresponding to the Cv value ofthe main fuel flow rate control valve 17 calculated with the multiplier115 based on the function of the aperture of the main fuel flow ratecontrol valve and the Cv value as shown in FIG. 26, which is set up inadvance in the preliminary studies (the specifications of the controlvalve). Then, the aperture of the main fuel flow rate control valve isoutputted as the main fuel flow rate control valve position commandvalue (the fuel flow rate control valve position command setting means).

Thereafter, the gas turbine combustion control device 41 controls themain fuel gas flow rate by regulating the aperture of the main fuel flowrate control valve 17 based on the main fuel flow rate control valveposition command value calculated in accordance with this computationlogic.

Next, the fuel gas temperature correction logic and the manifoldpressure correction logic functioning as correction logic in the eventof anomalies of instruments will be described.

First, the fuel gas temperature correction logic will be described withreference to FIG. 29. The actual measurement value of the fuel gastemperature is inputted to a lag time setter 122 and a switch 123,respectively. Here, when the multiple fuel gas thermometers Tf areinstalled (when the gas thermometers Tf are multiplexed), the actualmeasurement value of the fuel gas temperature is inputted via a lowervalue selector 121. The lower value selector 121 selects and outputs thelowest value out of the values measured by the multiple fuel gasthermometers Tf (two thermometers in the illustrated example).

The lag time setter 122 outputs the actual measurement value of the fuelgas temperature, which is inputted from the fuel gas thermometer Tf,after passage of predetermined lag time L since the actual measurementvalue is inputted. When an instrument anomaly signal is not inputtedfrom an instrument anomaly detection device (not shown) for detecting ananomaly of the fuel gas thermometer Tf attributable to disconnection orthe like, the switch 123 usually outputs the actual measurement value ofthe fuel gas temperature which is inputted from the fuel gas thermometerTf (inputted directly without interposing the lag time setter 122). Onthe contrary, if the instrument anomaly signal is inputted, the switch123 changes a route to the lag time setter 122, and outputs the inputtedvalue through this lag time setter 122. Here, the output value from thelag time setter 122 may vary depending on the input value even afterthis switching operation attributable to the instrument anomaly signal.However, the switch 123 holds and continues to output the value of thefuel gas temperature inputted from the lag time setter 122 at the pointof the switching operation attributable to the instrument anomalysignal. In other words, after the switching operation attributable tothe instrument anomaly signal, the constant value of the fuel gastemperature is outputted from the switch 123.

The output from the switch 123 is inputted to a primary delay operator124 functioning as a first primary delay operator and to a primary delayoperator 125 functioning as a second primary delay operator,respectively. A primary delay time constant set in the primary delayoperator 125 for a rate decrease is smaller than a primary delay timeconstant set in the primary delay operator 124 for a rate increase. Theprimary delay operator 124 performs a primary delay calculation in termsof the fuel gas temperature inputted from the switch 123, and theprimary delay operator 125 also performs a primary delay calculation interms of the fuel gas temperature inputted from the switch 123. Then,the lower value selector 126 selects and outputs a smaller value out ofa result of operation by the primary delay operator 124 and a result ofoperation by the primary delay operator 125.

When a rated speed (rated revolution) achievement signal is not inputtedfrom an unillustrated gas turbine revolution detection device (that is,when the gas turbine 1 is accelerating), a rating switch 127 selects theconstant value of the fuel gas temperature set in a signal generator 128and outputs the constant value to the function generator 103 of the flowrate control valve position command value computation logic shown inFIG. 24. On the contrary, when the rated speed achievement signal isinputted, the rating switch 127 selects the output of the lower valueselector 126 and outputs that value to the function generator 103 of thesame computation logic. Here, in order to prevent a rapid change in thefuel gas temperature, the rating switch 127 increases or decreases theoutput at a given rate when switching the selected signal from theoutput of the signal generator 128 to the output of the lower valueselector 126 or vice versa.

Next, the manifold pressure correction logic will be described. Asdescribed previously, the correction of the manifold pressure takesplace in terms of the pilot manifold pressure, the top hat manifoldpressure, and the main manifold pressure (see the manifold pressurecorrection logic 130, 140 or 150 in FIG. 24). Nevertheless, the schemesof the manifold pressure correction logic 130, 140, and 150 are similar.Accordingly, individual illustration and explanation will be omittedherein, and the contents of processing in these schemes of the manifoldpressure correction logic 130, 140, and 150 will be described alltogether.

As shown in FIG. 30, when an instrument anomaly signal is not inputtedfrom an instrument anomaly detection device (not shown) for detecting ananomaly of the pilot manifold pressure gauge PX2 (or any of the top hatmanifold pressure gauge PX3 and the main manifold fuel differentialpressure gauge PDX1) attributable to disconnection or the like, a switch161 usually outputs the actual measurement value of pilot manifoldpressure (or any of the top hat manifold pressure and the main manifoldpressure) inputted from the pilot manifold pressure gauge PX2 (or any ofthe top hat manifold pressure gauge PX3 and the main manifolddifferential pressure gauge PDX1) to a change rate setter 162. On thecontrary, if the instrument anomaly signal is inputted, the switch 161changes a route to manifold pressure computation logic 163 functioningas pressure computing means, and outputs a calculated value of the pilotmanifold pressure (or any of the top hat manifold pressure and the mainmanifold pressure) inputted from this manifold pressure computationlogic 163 to the change rate setter 162.

The change rate setter 162 sets up the change rate based on a functionof the power generator output (the gas turbine output) and the changerate as shown in FIG. 31 as an example, which is set up in advance inthe preliminary studies (the gas turbine designing processes) as well asbased on an actual measurement value or a command value of the powergenerator output (the gas turbine output). Then, based on that changerate, the change rate setter 162 restricts the rate of change in termsof either the actual measurement value or the calculated value of thepilot manifold pressure (or any of the top hat manifold pressure and themain manifold pressure) to be inputted from the switch 161 and outputtedto the function generator 102 (or any of the function generator 107 andthe function generator 114) of the flow rate control valve positioncommand value computation logic shown in FIG. 24.

In the case of an anomaly other than a choke, the manifold pressurecomputation logic 163 calculates the pilot manifold pressure (or any ofthe top hat manifold pressure and the main manifold pressure) based onthe following formula (6) obtained by modifying the following formula(5) that represents the Cv value calculation formula for an anomalyother than a choke. Meanwhile, in the case of an anomaly attributable toa choke, the manifold pressure computation logic 163 calculates thepilot manifold pressure (or any of the top hat manifold pressure and themain manifold pressure) based on the following formula (8) obtained bymodifying the following formula (7) that represents the Cv valuecalculation formula for an anomaly attributable to a choke.

$\begin{matrix} \begin{matrix}{{Cv} = {\frac{aG}{289}\sqrt{\frac{\gamma( {t + 273} )}{P_{1}^{2} - P_{3}^{2}}}}} \\{a = {\frac{1}{\gamma_{N}} \cdot \frac{273 + 15.6}{273}}}\end{matrix} \} & (5) \\ \begin{matrix}{P_{2} = \sqrt{( {\frac{aG}{289} \cdot \sqrt{\gamma( {t + 273} )}} )^{2} + P_{3}^{2}}} \\{a = {\frac{1}{\gamma_{N}} \cdot \frac{273 + 15.6}{273}}}\end{matrix} \} & (6) \\ \begin{matrix}{{Cv} = \frac{{aG}\sqrt{\gamma( {t + 273} )}}{250\; P_{2}}} \\{a = {\frac{1}{\gamma_{N}} \cdot \frac{273 + 15.6}{273}}}\end{matrix} \} & (7) \\ \begin{matrix}{P_{2} = {\frac{aG}{250{Cv}}\sqrt{\gamma( {t + 273} )}}} \\{a = {\frac{1}{\gamma_{N}} \cdot \frac{273 + 15.6}{273}}}\end{matrix} \} & (8)\end{matrix}$

In the formula (5) and the formula (6), reference code Cv denotes the Cvvalue of the pilot nozzle 25 (or any of the top hat nozzle 27 and themain nozzle 26). A preset constant value or a correction value correctedby a learning circuit (to be described later in detail) is applied tothis Cv value. Reference code t denotes the temperature of the pilotfuel gas (or any of the top hat fuel gas and the main fuel gas) ejectedfrom the pilot nozzle 25 (or any of the top hat nozzle 27 and the mainnozzle 26). A value measured with the fuel gas thermometer Tf is appliedto any of these fuel gas temperatures. Reference code γ denotes a gasdensity ratio relative to the air, which is a preset value.

Reference code G denotes the pilot fuel gas flow rate (the weight flowrate) (or any of the top hat fuel gas flow rate (the weight flow rate)and the main fuel gas flow rate (the weight flow rate)) ejected from thepilot nozzle 25 (or any of the top hat nozzle 27 and the main nozzle26). The pilot fuel gas flow rate G_(fPL) calculated with the functiongenerator 101 (or any of the top hat fuel gas flow rate G_(fTH)calculated with the function generator 106 and the main fuel gas flowrate G_(fMA) calculated with the function generator 113) of the flowrate control valve position command value computation logic in FIG. 24is applied to any of these fuel gas flow rates.

Note that the pilot fuel gas flow rate G_(fPL) (or any of the top hatfuel gas flow rate G_(fTH) and the main fuel gas flow rate G_(fMA))represents the total pilot fuel gas flow rate G_(fPL) (or any of thetotal top hat fuel gas flow rate G_(fTH) and the total main fuel gasflow rate G_(fMA)). A result of distribution of the relevant fuel gasflow rate to the respective pilot nozzles 25 (or any of the respectivetop hat nozzles 27 and the respective main nozzles 26) is equivalent tothe fuel gas flow rate of each of the pilot nozzles 25 (or any of eachof the top hat nozzles 27 and each of the main nozzles 26). Therefore, avalue obtained by dividing the pilot fuel gas flow rate G_(fPL) (or anyof the top hat fuel gas flow rate G_(fTH) and the main fuel gas flowrate G_(fMA)) by the number of the pilot nozzles 25 (or any of the tophat nozzles 27 and the main nozzles 26) is used as the pilot fuel gasflow rate (or any of the top hat fuel gas flow rate and the main fuelgas flow rate) G of each of the pilot nozzles 25 (or any of each of thetop hat nozzles 27 and each of the main nozzles 26). Reference code adenotes a coefficient used for converting any of these fuel gas flowrates G into a volume flow rate (m³/h) at 15.6° C. and at 1 ata. Thecoefficient a is a preset value. Reference code γ_(N) denotes gasdensity in a normal state.

Moreover, in the formula (5) and formula (6), reference code P₃ denotesa back pressure (a pressure on a downstream side) of the pilot nozzle 25(or any of the top hat nozzle 27 and the main nozzle 26). A measurementvalue of the cylinder pressure gauge PX5 is applied to this backpressure (see FIG. 3). Reference code P₂ denotes a front pressure (apressure on an upstream side) of the pilot nozzle 25 (or any of the tophat nozzle 27 and the main nozzle 26), i.e. the pilot manifold pressure(or any of the top hat manifold pressure and the main manifoldpressure).

In terms of explanation based on computation logic shown in FIG. 32, amultiplier 164 multiplies the Cv value (the constant value) of the pilotnozzle 25 (or any of the top hat nozzle 27 and the main nozzle 26)preset in a signal generator 165 by a correction coefficient (to bedescribed later in detail) calculated by the learning circuit 166 aslearning means. A function generator 167 performs a calculation inaccordance with the following formula (9) based on the actualmeasurement value of the fuel gas temperature (any one of the pilot fuelgas temperature t, the top hat fuel gas temperature t, and the main fuelgas temperature t). A multiplier 168 multiplies the pilot fuel gas flowrate G (or any of the top hat fuel gas flow rate G and the main fuel gasflow rate G), which is obtained based on the pilot fuel gas flow rateG_(fPL) calculated with the function generator 101 (or any of the tophat fuel gas flow rate G_(fTH) calculated with the function generator106 and the main fuel gas flow rate G_(fMA) calculated with the functiongenerator 113) of the flow rate control valve position command valuecomputation logic in FIG. 24, by a result of calculation with thefunction generator 164. A divider 169 divides a result of multiplicationwith the multiplier 168 by a result of multiplication with themultiplier 164.√{square root over (γ(t+273))}  (9)

A multiplier 171 multiplies a result of division with the divider 169 bya value obtained by the following formula (10) which is set in a signalgenerator 170:

$\begin{matrix}{\frac{1}{\gamma_{N}} \cdot \frac{273 + 15.6}{273} \cdot \frac{1}{289}} & (10)\end{matrix}$

A multiplier 172 multiplies a result of multiplication with themultiplier 171 by the same value (i.e., the multiplier 172 calculates asquare of the result of multiplication with the multiplier 171). Anadder 173 adds the value (1.0332) set in a signal generator 174 to theactual measurement value of the cylinder pressure (used as the backpressure P₂ of the pilot nozzle, the top hat nozzle or the main nozzle)and forms the cylinder pressure being the measurement value of thecylinder pressure gauge PX5 into an absolute pressure. A multiplier 175multiplies a result of addition with the adder 173 by the same value(i.e., the multiplier 175 calculates a square of the cylinder pressureP₂). An adder 176 adds a result of multiplication with the multiplier172 to a result of multiplication with the multiplier 175. That is, acalculation in accordance with the following formula (11) is completedby the time of the processing with this adder 176. Then, a rooter 177calculates a root of a result of addition with the adder 176. That is,the calculation in accordance with the above-described formula (6) iscompleted by the time of the processing with this rooter 177. In thisway, a calculated value P₂ in terms of the pilot manifold pressure (orany of the top hat manifold pressure and the main manifold pressure) inthe case of an anomaly other than a choke is obtained.

$\begin{matrix}{( {\frac{aG}{289} \cdot \sqrt{\gamma( {t + 273} )}} )^{2} + P_{3}^{2}} & (11)\end{matrix}$

Meanwhile, a multiplier 179 multiplies the result of division by theabove-described divider 169 by a value obtained by the following formula(12) which is set in a signal generator 178. That is, the calculation inaccordance with the above-described formula (8) is completed by the timeof the processing with this multiplier 179. In this way, the calculatedvalue P₂ in terms of the pilot manifold pressure (or any of the top hatmanifold pressure and the main manifold pressure) in the case of ananomaly attributable to a choke is obtained.

$\begin{matrix}{\frac{1}{\gamma_{N}} \cdot \frac{273 + 15.6}{273} \cdot \frac{1}{250}} & (12)\end{matrix}$

A choke identifier 180 compares the pilot manifold pressure (or any ofthe top hat manifold pressure and the main manifold pressure) P₂ that isthe output of the rooter 177 with the cylinder pressure (the backpressure of any of the pilot nozzle, the top hat nozzle, and the mainnozzle) P₃ that is the output of the adder 173, and identifies a chokewhen the condition as defined in the following formula (13) issatisfied:

$\begin{matrix}{P_{3} \leq {\frac{1}{2}P_{2}}} & (13)\end{matrix}$

A switch 181 selects the output value of the multiplier 179 when thechoke identifier 180 identifies the choke, and outputs that value to theswitch 161 in FIG. 30 as the calculated pilot manifold pressure (or anyof the calculated top hat manifold pressure and the calculated mainmanifold pressure) P₂. On the contrary, the switch 181 selects theoutput value of the rooter 177 when the choke identifier 180 does notidentify the choke, (in the case of an anomaly other than a choke), andoutputs that value to the switch 161 in FIG. 30 as the calculated pilotmanifold pressure (or any of the calculated top hat manifold pressureand the calculated main manifold pressure) P₂.

Next, the learning circuit 166 will be described with reference to FIG.33. As similar to the case of the learning circuit 62, the learningcircuit 166 firstly judges whether or not the combustion gas temperatureTIT reaches the maximum combustion gas temperature (1500° C.) beforestarting to learn the nozzle Cv value. Specifically, when the combustiongas temperature TIT at the inlet of the gas turbine is equal to themaximum combustion gas temperature (1500° C.), there is the relationbetween the pressure ratio of the compressor 4 (the ratio between thepressure on the inlet side and the pressure on the outlet side of thecompressor 4) and the exhaust gas temperature as shown in FIG. 18.Therefore, the learning circuit 166 monitors the pressure ratio (thecylinder pressure/the intake-air pressure) of the compressor 4 obtainedfrom the actual measurement value of the intake-air pressure and theactual measurement value of the cylinder pressure as well as the actualmeasurement value of the exhaust gas temperature. Moreover, the learningcircuit 62 judges that the combustion gas temperature TIT at the inletof the gas turbine reaches the maximum combustion gas temperature (1500°C.) when the pressure ratio and the exhaust gas temperature satisfy therelation shown in FIG. 18, and then starts learning. It is to be noted,however, that the present invention will not be limited only to thisconfiguration. For example, it is also possible to start learning beforethe combustion gas temperature TIT at the inlet of the gas turbinereaches the maximum combustion gas temperature (1500° C.).

When the learning circuit 166 starts learning, a subtracter (a deviationoperator) 182 firstly calculates a deviation between the pilot manifoldpressure (or any of the top hat manifold pressure and the main manifoldpressure) P₂ calculated in accordance with the manifold pressurecorrection logic 163 and the pilot manifold pressure (or any of the tophat manifold pressure and the main manifold pressure) measured with themain manifold pressure gauge PX2 (or any of the top hat manifoldpressure gauge PX3 and the main manifold pressure gauge PX1).

Thereafter, a PI controller 183 performs proportional and integraloperations based on the deviation to calculate the correctioncoefficient in a range from 0 to 1. This correction efficient isoutputted to the multiplier 164 of the manifold pressure correctionlogic 163 in FIG. 32 and is then multiplied by the nozzle Cv value (thefixed value) set in the signal generator 165. In this way, by correctingthe nozzle Cv value so as to eliminate the deviation between thecalculated value of the pilot manifold pressure (or any of the top hatmanifold pressure and the main manifold pressure) P₂ and the actualmeasurement value of the pilot manifold pressure (or any of the top hatmanifold pressure and the main manifold pressure). Accordingly it ispossible to obtain a more accurate nozzle Cv value.

(Operation Effects)

As described above, according to the gas turbine combustion controldevice 41 of this embodiment, the 700° C. MW value and the 1500° C. MWvalue are calculated based on the IGV aperture, the intake-airtemperature, and the atmospheric pressure ratio. Then, based on thesevalues and on the actual measurement value of the power generator output(the gas turbine output), the CLCSO to render the combustion gastemperature at the inlet of the gas turbine dimensionless is computed bydirect interpolation. Thereafter, the apertures of the pilot fuel flowrate control valve 19, the top hat fuel flow rate control valve 21, andthe main fuel flow rate control valve 17 are controlled based on therespective fuel gas ratios (the pilot ratio, the top hat ratio, and themain ratio), which are determined based on this CLCSO. In this way, thefuel supplies to the respective fuel nozzles (the pilot nozzle 25, thetop hat nozzle 27, and the main nozzle 26) are controlled. Accordingly,it is possible to perform the control based on the combustion gastemperature at the inlet of the gas turbine in conformity to theoriginal concept, and to maintain the relations between the CLCSO andthe respective fuel gas ratios (the pilot ratio, the top hat ratio, andthe main ratio), i.e. the relations between the combustion gastemperature and the respective gas ratios (the pilot ratio, the top hatratio, and the main ratio) even if the intake-air temperature, thecombustion gas temperature, and the properties of the combustion gas arechanged or if the performance of the gas turbine 1 is deteriorated. As aresult, it is possible to perform more appropriate combustion controlthan a conventional combustion control device.

Moreover, according to the gas turbine combustion control device 41 ofthis embodiment, the bypass amount of the compressed air is controlledby regulating the aperture of the combustor bypass valve based on thecomputed CLCSO. Accordingly, it is possible to control the combustorbypass valve 8 based on the combustion gas temperature at the inlet ofthe gas turbine in conformity to the original concept as well. Moreover,it is possible to maintain the relation between the CLCSO and theaperture of the combustor bypass valve, i.e. the relation between thecombustion gas temperature at the inlet of the gas turbine and theaperture of the combustor bypass valve. As a result, it is possible toperform more appropriate combustion control than a conventionalcombustion control device in light of the bypass amount control of thecompressed air as well.

For example, when carrying out an IGV opening operation at the constantpower generator output (the gas turbine output), it is apparent fromoperating results of the gas turbine as shown in FIG. 34 to FIG. 36 thatthe pilot ratio and the aperture of the combustor bypass valve follow adecline in the combustion gas temperature TIT at the inlet of the gasturbine attributable to the IGV opening operation. Moreover, it is alsoapparent from operating results of the gas turbine as shown in FIG. 37and FIG. 38 that a variation in the combustion gas temperature does notcause a variation in the pilot ratio or in the aperture of the combustorbypass valve.

Further, according to the gas turbine combustion control device 41 ofthis embodiment, the fuel gas ratios (the pilot ratio, the top hatratio, and the main ratio) are corrected based on the intake-airtemperature. Accordingly, it is possible to carry out more appropriatecombustion control relative to a variation in the intake-airtemperature. Moreover, the intake-air temperature correction amount isadjusted in response to the CLCSO in this case. Therefore, it ispossible to perform appropriate intake-air temperature correction inresponse to the load (the power generator output: the gas turbineoutput).

Meanwhile, the gas turbine combustion control device 41 of thisembodiment includes the learning circuit 62 configured to compare thecomputed 1500° C. MW value with the actual measurement value of thepower generator output (the gas turbine output) based on the actualmeasurement value of the exhaust gas temperature and the measurementafter the judgment that the combustion gas temperature at the inlet ofthe gas turbine reaches the maximum temperature (1500° C.), and then tocorrect the 1500° C. MW value to coincide with the actual measurementvalue of the power generator output (the gas turbine output).Accordingly, even when the performance of the gas turbine 1 isdeteriorated, it is possible to maintain the relations between the CLCSO(the combustion gas temperature at the inlet of the gas turbine) and therespective fuel gas ratios (the pilot ratio, the top hat ratio, and themain ratio) and the relation between the CLCSO (the combustion gastemperature at the inlet of the gas turbine) and the aperture of thecombustor bypass valve.

Furthermore, according to the gas turbine combustion control device 41of this embodiment, the fuel flow rate command values (the PLCSO, theTHCSO, and the MACSO) for the respective types of the fuel gas arecalculated based on the total fuel flow rate command value (the CSO) andthe fuel gas ratios (the pilot ratio, the top hat ratio, and the mainratio). Then, the fuel gas flow rates (the pilot fuel gas flow rateG_(fPL), the top hat fuel gas flow rate G_(fTH), and the main fuel gasflow rate G_(fMA)) are calculated based on the function of the fuel flowrate command value and the fuel gas flow rate. Thereafter, the Cv valuesof the respective fuel flow rate control valves 17, 19, and 21 arecalculated in accordance with the Cv value calculation formula based onthe fuel gas flow rates, the fuel gas temperature, and the front andback pressures of the respective fuel flow rate control valves 17, 19,and 21. Then, the respective fuel flow rate control valve positioncommand values (the pilot fuel flow rate control valve position commandvalue, the top hat fuel flow rate control valve position command value,and the main fuel flow rate control valve position command value) arecalculated based on the Cv values and on the function between the Cvvalue and the aperture of the fuel flow rate control valve. Accordingly,it is possible to automatically determine the apertures of therespective fuel flow rate control valves 17, 19, and 21 so as to meetthe predetermined fuel gas ratios (the pilot ratio, the top hat ratio,and the main ratio). That is, as long as the fuel gas ratios (the pilotratio, the top hat ratio, and the main ratio) are inputted, it ispossible to calculate the respective fuel flow rate control valveposition command values (the pilot fuel flow rate control valve positioncommand value, the top hat fuel flow rate control valve position commandvalue, and the main fuel flow rate control valve position command value)corresponding to the fuel gas ratios automatically.

Meanwhile, according to the gas turbine combustion control device 41 ofthis embodiment, when an anomaly occurs in the fuel gas thermometer Tf,the fuel gas temperature correction logic 120 applies the actualmeasurement value of the fuel gas temperature at a certain time periodprior to occurrence of such an anomaly. Therefore, it is possible toperform stably combustion control and to continue operation of the gasturbine 1 without causing a rapid change in the combustion gas flow rateand the like even when the anomaly such as disconnection occurs in thefuel gas thermometer Tf.

Moreover, according to the gas turbine combustion control device 41 ofthis embodiment, the fuel gas temperature correction logic 120 includesthe primary delay operator 124 and the primary delay operator 125 thathas a smaller primary delay time constant than a primary delay constantof the primary delay operator 124. In terms of the fuel gas temperature,the primary delay operator 124 and the primary delay operator 125perform primary delay operations, and a smaller value out of the resultsof such operations is used as the combustion gas temperature. Therefore,it is possible to relax a change a change rate of the combustion gastemperature at the inlet of the gas turbine and to prevent excessiveinfusion of the fuel gas.

Moreover, the gas turbine combustion control device 41 of thisembodiment includes the manifold pressure computation logic 163 forcomputing the back pressures of the respective fuel flow rate controlvalves (the pilot fuel flow rate control valve 19, the top hat fuel flowrate control valve 21, and the main fuel flow rate control valve 17)corresponding to the front pressures of the respective fuel nozzles inaccordance with the computational formula of the front pressures of therespective fuel nozzles derived from the Cv value computational formulaof the respective fuel nozzles based on the fuel gas flow rates of therespective fuel nozzles (the pilot nozzle 25, the top hat nozzle 27, andthe main nozzle 26) that are obtained from the respective fuel gas flowrates (the pilot fuel gas flow rate G_(fPL), the top hat fuel gas flowrate G_(fTH), and the main fuel gas flow rate G_(fMA)), the Cv values ofthe respective fuel nozzles, the fuel gas temperature, and the backpressures of the fuel nozzles. In addition, the gas turbine combustioncontrol device 41 includes the manifold pressure correction logic 130,140, and 150 for using the pressures computed with this manifoldpressure computation logic 163 as the back pressures of the respectivefuel flow rate control valves when an anomaly occurs in any of therespective pressure gauges (the pilot manifold pressure gauge PX2, thetop hat manifold pressure gauge PX3, and the main manifold pressuregauge PX1) for measuring the back pressures of the respective fuel flowrate control valves. Therefore, even when an anomaly such asdisconnection occurs in any of the pressure gauges (the pilot manifoldpressure gauge PX2, the top hat manifold pressure gauge PX3, and themain manifold pressure gauge PX1), it is possible to perform combustioncontrol of the gas turbine 1 and thereby to continue operation of thegas turbine 1.

Meanwhile, the gas turbine combustion control device 41 of thisembodiment includes the learning circuit 166 for comparing the backpressures of the respective fuel flow rate control valves (the pilotfuel flow rate control valve 19, the top hat fuel flow rate controlvalve 21, and the main fuel flow rate control valve 17) computed by themanifold pressure computation logic 163 with the actual measurementvalues of the back pressures (the pilot manifold pressure, the top hatmanifold pressure, and the main manifold pressure) of the respectivefuel flow rate control valves and for correcting the Cv values of therespective fuel nozzles (the pilot nozzle 25, the top hat nozzle 27, andthe main nozzle 26) such that the calculated values of the backpressures coincide with the actual measurement values of the backpressures. Therefore, it is possible to obtain more accurate Cv valuesand thereby to obtain the calculated values of the back pressures moreaccurately.

Here, the embodiment has been described as an example of the gas turbineincluding the combustor provided with three types of fuel nozzles,namely, a first fuel nozzle (corresponding to the main nozzle in theillustrated example), a second fuel nozzle (corresponding to the pilotnozzle in the illustrated example), and a third fuel nozzle(corresponding to the top hat nozzle in the illustrated example).However, the present invention will not be limited only to thisconfiguration. For example, the present invention is also applicable toa gas turbine including a combustor provided with two types of fuelnozzles (the first fuel nozzle and the second fuel nozzle), and to a gasturbine including a combustor provided with four types of fuel nozzles(the first fuel nozzle, the second fuel nozzle, the third nozzle, and afourth nozzle).

Moreover, the maximum fuel gas temperature is set to 1500° C. in theabove-described embodiment. Needless to say, the maximum fuel gastemperature is not limited only to this level, and it is possible to setthe maximum fuel gas temperature to any other levels such as 1400° C. or1600° C., as appropriate, in the course of gas turbine designingprocesses in light of improvement in efficiency, durability ofinstruments, NOx reduction, and the like.

Further, when the apertures of the fuel flow rate control valves arecontrolled based on the fuel ratios (the pilot ratio, the top hat ratio,and the main ratio) as described above, such controlling means is notlimited only to the means for setting the respective fuel flow ratecontrol valve position command values based on the fuel ratios (thepilot ratio, the top hat ratio, and the main ratio) as described in theembodiment. It is also possible to perform control based on otherarbitrary controlling means.

The present invention is applicable to and useful for the case ofinstalling a combustion control device for a gas turbine which is fittedto a gas turbine provided with a gas turbine body, a combustor havingmultiple types of fuel nozzles, a compressor having an inlet guide vane,and multiple fuel flow rate control valves for respectively controllingfuel supplies to the multiple types of the fuel nozzles, and isconfigured to control the fuel supplies to the multiple types of thefuel nozzles by controlling apertures of the fuel flow rate controlvalves.

The invention thus described, it will be obvious that the same may bevaried in many ways. Such variations are not to be regarded as adeparture from the spirit and scope of the invention, and all suchmodifications as would be obvious to one skilled in the art are intendedto be included within the scope of the following claims.

1. A combustion control device for a gas turbine which is fitted to agas turbine provided with a gas turbine body, a combustor havingmultiple types of fuel nozzles, a compressor having an inlet guide vane,and multiple fuel flow rate control valves for respectively controllingfuel supplies to the multiple types of the fuel nozzles, and which isconfigured to control the fuel supplies to the multiple types of thefuel nozzles by controlling apertures of the fuel flow rate controlvalves, the combustion control device comprising: first gas turbineoutput computing means for computing a first gas turbine outputcorresponding to a first combustion gas temperature at an inlet of thegas turbine based on an intake-air temperature of the compressor and anaperture of the inlet guide vane; second gas turbine output computingmeans for computing a second gas turbine output corresponding to asecond combustion gas temperature at the inlet of the gas turbine higherthan the first combustion gas temperature at the inlet of the gasturbine based on the intake-air temperature of the compressor and theaperture of the inlet guide vane; and combustion load command computingmeans for computing a combustion load command value to render thecombustion gas temperature at the inlet of the gas turbine dimensionlessby direct interpolation based on the first gas turbine output computedby the first gas turbine output computing means, the second gas turbineoutput computed by the second gas turbine output computing means, and anoutput of the gas turbine, wherein ratios of fuels to be suppliedrespectively to the multiple types of the fuel nozzles are determinedbased on the combustion load command value computed by the combustionload command computing means, and the fuel supplies to the multipletypes of the fuel nozzles are controlled by controlling apertures of thefuel flow rate control valves based on the ratio of the fuels.
 2. Thecombustion control device for a gas turbine according to claim 1,wherein the gas turbine includes a combustor bypass valve for adjustinga bypass amount of compressed air around the combustor, and the bypassamount of the compressed air is regulated by controlling an aperture ofthe combustor bypass valve based on the combustion load command valuecomputed by the combustion load command computing means.
 3. Thecombustion control device for a gas turbine according to claim 1,wherein the gas turbine includes gas turbine bypassing means forbypassing compressed air around any of the combustor and the gas turbinebody, the first gas turbine output computing means computes the firstgas turbine output based on the intake-air temperature of thecompressor, the aperture of the inlet guide vane, and a turbine bypassratio equivalent to a ratio between a total amount of compressed air bythe compressor and a turbine bypass flow rate by the gas turbinebypassing means, and the second gas turbine output computing meanscomputes the second gas turbine output based on the intake-airtemperature of the compressor, the aperture of the inlet guide vane, andthe turbine bypass ratio.
 4. The combustion control device for a gasturbine according to claim 1, wherein the first gas turbine outputcomputing means computes the first gas turbine output based on theintake-air temperature of the compressor, the aperture of the inletguide vane, and an atmospheric pressure ratio equivalent to a ratiobetween an intake pressure of the compressor and a standard atmosphericpressure or computes the first gas turbine output based on theintake-air temperature of the compressor, the aperture of the inletguide vane, the turbine bypass ratio, and the atmospheric pressureratio, and the second gas turbine output computing means computes thesecond gas turbine output based on the intake-air temperature of thecompressor, the aperture of the inlet guide vane, and the atmosphericpressure ratio or computes the second gas turbine output based on theintake-air temperature of the compressor, the aperture of the inletguide vane, the turbine bypass ratio, and the atmospheric pressureratio.
 5. The combustion control device for a gas turbine according toclaim 1, further comprising: intake-air temperature correcting means forcorrecting the ratios of fuels based on the intake-air temperature ofthe compressor.
 6. The combustion control device for a gas turbineaccording to claim 5, wherein the intake-air temperature correctingmeans adjusts an intake-air temperature correction amount in response tothe combustion load command value.
 7. The combustion control device fora gas turbine according to claim 1, wherein the second gas turbineoutput computing means computes the second gas turbine outputcorresponding to a maximum combustion gas temperature equivalent to thesecond combustion gas temperature at the inlet of the gas turbine, andthe combustion control device comprises learning means for comparing thesecond gas turbine output computed by the second gas turbine outputcomputing means and an output of the gas turbine after a judgment thatthe combustion gas temperature at the inlet of the gas turbine reachesthe maximum combustion gas temperature based on a temperature of exhaustgas discharged from the gas turbine body and on a pressure ratio of thecompressor, and correcting the second gas turbine output so as tocoincide with the output of the gas turbine.